JPS5855384B2 - Fluid pressure operated power transmission device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention includes a fluid pressure motor operated by pressurized fluid;
This is a fluid pressure operated power transmission device equipped with a fluid pump driven by this motor, and even if the input flow rate increases or decreases, an output flow rate proportional to this can always be obtained, and it has high versatility. In addition, the input fluid and output fluid are completely cut off, and the rotary operating parts do not come into contact with the input and output fluids, and there is no leakage, and furthermore, no electrical equipment dedicated to electric uppers or electric control elements is used. The object of the present invention is to obtain the above-mentioned device which is inexpensive and energy-saving with few failures.

An embodiment of the present invention will be described below with reference to the drawings.

Reference numeral 1 denotes a fluid pressure motor driven by the hydraulic pressure of pressurized fluid branched from the main stream flowing in a chemical process, etc., and a speed reducer 2 and a fluid pump 3 are sequentially disposed above it.

The casing 4 of the fluid pressure motor 1 consists of a motor body 5 having a cylindrical hollow chamber A with an open top, and a lid 6 covering the top opening.

The output shaft 7 passes through the center of the hollow chamber A, and its upper and lower ends are rotatably supported by the lid 6 and the bottom surface of the motor body 5 via bearings 8 and 9, respectively.

The interior of the hollow chamber A is divided into upper and lower chambers by an annular plate 10, and inside the upper and lower chambers A1 and A2, there are first and second chambers that apply rotational force to the output shaft 7 with a phase shift of 180° from each other. Driving units 11a and 11b are provided.

Since the first and second driving parts 11a and 11b have the same components, the first driving part 11a will be described in detail.
As shown in the figure, a fluid supply port 12 and a fluid discharge port 13 are formed in the peripheral wall of the upper chamber A1 in parallel and close to each other, and an annular motor is provided on the inner peripheral surface of the upper chamber A1 passing through the inner opening. A chamber 14 is formed.

The output shaft 7 is attached to the circumferential surface of the output shaft 7 located in the upper chamber A1.
a notched groove 15 having a bottom plane 15a parallel to the longitudinal axis of the
is formed.

An eccentric ring 16 is disposed around the notch groove 15 with a bearing 17 on its inner circumferential surface, and between the bottom plane 15a of the notch groove 15 and the inner circumferential surface of the bearing 17. A half-moon-shaped wedge roller 18 is interposed, and an eccentric amount E1 exists between the axis of the output shaft 7 and the axis of the eccentric ring 16.

These eccentric wheels 16, bearings 17, and wedge rollers 18 constitute an eccentric power transmission mechanism for the output shaft 7.

An endless elastic diaphragm 19 made of rubber or the like as a rotational force transmission medium is attached to the entire inner peripheral surface of the upper chamber A1, and the diaphragm 19 is connected to the upper chamber A by an eccentric ring 16.
, is crimped onto the inner surface of the .

The diaphragm 19 is connected to the upper chamber A1 by a bolt 20 and a nut 21 between the supply port 12 and the discharge port 13.
It is fixed to the peripheral wall of the motor chamber 14 and partitions the motor chamber 14 into a supply side and a discharge side.

In the second driving unit 11b, the same parts as those in the first driving unit 11a are given the same reference numerals, but the wedge roller 18
The position of the V-th driving unit 11a is symmetrical with respect to the axis of the output shaft 7.

Further, the fluid supply port and the fluid discharge port are respectively parallel to the fluid supply port 12 and the fluid discharge port 13 of the first driving portion 11a.

22 to 24 are spacers interposed between each bearing 8, 9, and 17.

The casing 25 of the reducer 2 is connected to the lid 6 of the fluid pressure motor 1.
It shares the casing body 26 of the fluid pump 3 and the fluid pump 3, with an annular plate 27 interposed between them, and a planetary gear mechanism is housed inside.

The planetary gear mechanism includes a sun gear 28 fitted to the upper protruding end of the bearing 8 of the output shaft 7, and an internal ring gear 29 located on the outer periphery of the sun gear 28 and fixed by the annular plate 27 and the lid 6. and a planetary gear 30 that meshes with both gears 28 and 29,
It consists of a disk 31 that is fixed to a pump shaft 37, which will be described later, and rotatably supports the planetary gear 30.

The casing 32 of the fluid pump 3 consists of the main body 26 having a cylindrical hollow chamber B with an open top, and a lid 33 that covers the top opening.

As shown in FIG. 3, a liquid suction port 34 is provided on the peripheral wall of the main body 26.
and the liquid discharge port 35 are formed to face each other, and the main body 26
An annular pump chamber 36 is formed on the inner peripheral surface and passes through the inner openings 34 and 35 on both sides.

The pump shaft 37 passes through the center of the hollow chamber B, and its upper and lower ends are rotatably supported by the inner surface of the lid body 33 and the bottom of the paralyzer body 26 via bearings 38 and 39, respectively.

The pump shaft 37 is connected from the bearing 39 to the casing 25 of the reducer 2.
It protrudes inward, and the protrusion has a disk 3 of the reducer 2.
1 abort is fixed.

An eccentric shaft portion 37a having a diameter larger than that of the pump shaft 37 is integrally formed in the intermediate portion of the pump shaft 37, and an eccentric amount E2 exists between the shaft center of the eccentric shaft portion 37a and the shaft center of the pump shaft 37.

A pair of upper and lower support plates 40 are attached to the eccentric shaft portion 37a of the pump shaft 37 via bearings 41, and base ends of a pair of left and right connecting rods 42 are pivoted via pivots 43 at both left and right ends of both plates 40. It will be worn.

Each tip of each connecting rod 42 is connected to the hollow chamber B via a suppression plate 45.
The pump shaft 37 is fixed to the inner circumferential surface of an endless elastic diaphragm 44 made of rubber or the like, which is attached to the entire inner circumferential surface of the pump shaft 37.
When rotates, the eccentric shaft portion 37a1 support plate 40, the connecting rod 42
, and the elastic diaphragm 44 via the pressing plate 45.
It is possible to apply intermittent pressing force to the

The eccentric shaft portion 37a1 support plate 40, bearing 41, connecting rod 42, and press plate 45 constitute an eccentric reciprocating mechanism that reciprocates as the pump shaft 37 rotates.

As shown in FIGS. 3 and 4, the pump shaft 37 has an eccentric shaft portion 3.
A pair of upper and lower support plates 46 and 46' are rotatably supported via bearings 47 and 48 so as to sandwich 7a.
, 46' extend radially in the direction of the suction port 34 and the discharge port 35, and each has a shaft 49 at each end thereof.
A roller 50 is rotatably supported via the roller.

Each roller 50 has the suction port 34 and the discharge port 3, respectively.
The inner surface of the diaphragm 44 facing the diaphragm 5 is pressed against the inner surface of the diaphragm 44 .

A crank mechanism C that can alternately control the opening and closing of the suction port 34 and the discharge port 35 by swinging each roller 50 by the rotation of the eccentric shaft portion 37a is connected to the pump shaft 37 and one support plate 46.
’.

The crank mechanism C includes a first gear 51 fitted to the pump shaft 37 at the lower part of the lower support plate 46, and the first gear 5
1 and a second gear 52 that meshes with the second gear 52.
A support shaft 52a protruding from the lower end surface of the pump casing body 26 is rotatably supported by the bottom surface of the pump casing body 26, and a cylindrical projection having an eccentric amount E3 with respect to the axis of the support shaft 52a is formed on the upper end surface of the second gear 52. A portion 52b protrudes, and this protrusion 5
2b is slidably fitted into a rectangular through hole 46a formed in the support plate 46.

The through hole 46a is formed to be long in the radial direction of the pump shaft 37, and rotation of the shaft 37 imparts a constant cycle of rocking motion to the support plate 46' via the first and second gears 5L52 and the protrusion 52b. .

The support plate 46', the roller 50, the crank mechanism C, and the like constitute an on-off valve mechanism that swings as the pump shaft 37 rotates.

Next, the operation of this embodiment will be explained.

When pressurized fluid branched from the main stream is supplied to each supply port 12 of the first and second driving parts 11a and 11b of the fluid pressure motor 1, a force in the circumferential direction is applied to the eccentric ring 16 via the diaphragm 19. do.

As a result, the eccentric wheel 16 receives a rotational force in the clockwise direction in FIG. 1
8, the output shaft 7 rotates in the same direction.

Transmission of the rotational force from the eleventh second driving parts 11a and 11b to the output shaft 7 is performed with less interruption due to the 180° phase shift, and the output shaft 7 rotates smoothly.

Further, the pressurized fluid that has completed its work is returned to the mainstream through each discharge port 13.

Due to the rotation of the output shaft T, the pump shaft 3 is
7 rotate at a reduced speed in the same direction.

This rotation of the pump shaft 37 causes the eccentric shaft portion 37a to rotate eccentrically, so that the left and right connecting rods 42 reciprocate in the left-right direction in FIG. When pressed, the space between the left half outer circumferential surface of the elastic diaphragm 44 and the left half inner circumferential surface of the hollow chamber B, that is, the inside of the left half of the pump chamber 36 becomes the discharge side, and at the same time, the right half circumference of the elastic diaphragm 44 becomes the right half circumference. between the right-hand half outer peripheral surface of the elastic diaphragm 44 and the right-hand inner peripheral surface of the hollow chamber B, that is, the pump chamber 36
The right half of is the suction side.

On the other hand, due to the rotation of the pump shaft 37, the first
The second gear 51°52 rotates, thereby causing the protrusion 52b to rotate.
slides in the through hole 46a, so when the left half of the pump chamber 36 becomes the discharge side, each roller 50 swings clockwise as shown in FIG. 35 is opened, the liquid between the left half of the pump chamber 36 is discharged to the outside from the discharge port 35, and at the same time, the fluid is sucked into the right half of the pump chamber 36 from the suction port 34.

Contrary to the above, when the right half of the pump chamber 36 becomes the discharge side and the left half becomes the suction side, each roller 50 is swung counterclockwise by the crank mechanism, and the fluid is discharged and
Each suction operation is performed.

At this point, the first. Second driving unit 11a.

Assuming that the amount of pressurized fluid supplied (actually the amount of discharge) required for one rotation of the output shaft I by 11b is 10, and the amount of fluid discharged twice per one rotation of the pump shaft 37 is 1, the fluid pressure motor 1 and the pump The ratio of the amount of both ridges in No. 3 is 10:1.

Further, if the reduction ratio of the reduction gear 2 is set to 1/10, the above ratio becomes 100:1.

Therefore, when the fluid pressure motor 1 is driven by a pressurized fluid branched from the mainstream, the pump 3 can perform proportional injection at a ratio of 1/100 to 100 of the mainstream, and the volume of the mainstream changes momentarily. Even if the ratio is constant, the ratio of 100:1 is always maintained because the rotational speed of the fluid pressure motor 1 and the pump 3 only changes in accordance with the change.

As described above, according to the present invention, it is possible to obtain a fluid pressure operated power transmission device that can always obtain an output flow rate proportional to the input flow rate even if the input flow rate increases or decreases. The discharge fluid of the pump and the operating parts of the fluid pressure motor and fluid pump are all fluid-tightly isolated by endless elastic diaphragms 19 and 44 as rotational force transmission media, and the elastic diaphragms 19 and 44 have high sealing performance. Therefore, there is no part where the fluid leaks, and it is possible to supply special fluids such as corrosive fluids and to drive using the fluids, making it extremely versatile.

Furthermore, since the device is leak-free, maintenance is easy, there is no loss in torque transmission, and accuracy is improved.

Furthermore, since there is no need for any drive or control by electric equipment such as an electric motor or electrical control elements, the structure is simple, there are few failures, and it is possible to reduce device costs and operating costs.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional front view of one embodiment of the present invention, and FIG.
Figure 3 is a cross-sectional view along the line ■-■, Figure 1 is a cross-sectional view along the line ■■,
The drawings are a sectional view taken along the line TV-IV in FIG. 1, and FIG. 5 is a diagram illustrating the suction and discharge actions of the pump. DESCRIPTION OF SYMBOLS 1... Fluid pressure motor, 3... Fluid pump, 4... Casing, 7... Output shaft, 12... Supply port, 13...Exhaust port,
14...Motor room, 16,17゜18...
...Eccentric shaft, bearing, wedge roller as eccentric power transmission mechanism, 19...Elastic diaphragm, 25...
...Casing, 34...Suction port, 35...
...Discharge port, 36...Pump chamber, 37...
...Pump shaft, 37a. 40.41.42.45...Eccentric shaft part, support plate, bearing, connecting rod, pressing plate, 44.
...Elastic diaphragm, 46', 50. C...
・・Support plate, roller, and crank mechanism as an on-off valve mechanism.

Claims (1)

[Claims] 1 Consisting of a fluid pressure motor operated by pressurized fluid and a fluid pump operated by receiving power from the fluid pressure motor, the fluid pressure motor communicates with a cylindrical hollow chamber. a casing having a pressurized fluid supply port and a discharge port; an output shaft rotatably supported by the casing; an endless elastic tire flam accommodated in the casing along an inner peripheral wall thereof; an annular motor chamber formed between the casing and the elastic diaphragm; and an annular motor chamber provided between the output shaft and the elastic diaphragm;
an eccentric power transmission mechanism capable of transmitting the pressure of pressurized fluid flowing in and out of the motor chamber to the output shaft as rotational force via the elastic diaphragm; a casing having a suction port and a discharge port communicating with the hollow chamber; a pump shaft rotatably supported within the casing and connected to the output shaft; an endless elastic diaphragm housed in such a manner; a pump chamber formed between the casing and the elastic diaphragm; and a pump chamber connected between the pump shaft and the elastic diaphragm so as to transmit the rotational force of the pump shaft through the elastic diaphragm. an eccentric reciprocating mechanism configured to transmit a pumping action to the pump chamber; connected between the output shaft and the eccentric reciprocating mechanism, the mechanism opens and closes the suction port and the discharge port at predetermined timings via the elastic diaphragm; A fluid pressure operated power transmission device comprising an operating on-off valve mechanism.