WO2003006827A1

WO2003006827A1 - Rotary fluid energy converter

Info

Publication number: WO2003006827A1
Application number: PCT/JP2002/006820
Authority: WO
Inventors: Yasuo Kita
Original assignee: Yasuo Kita
Priority date: 2001-07-11
Filing date: 2002-07-04
Publication date: 2003-01-23
Also published as: JP2005054574A

Abstract

A rotary fluid energy converter capable of eliminating the need of a large capacity rolling bearing by canceling a bearing load with a couple formed by a fluid pressure, wherein a static pressure pad (6) held by a casing (5) is installed on the outside of a polygon ring (4) in the direction perpendicular to the eccentric direction of a pintle (1), and a pressure received by a cylinder (21) around the halfway of the pad is led into a hold hole (51), and the couple is formed with an inward force (F) caused by bringing the static pressure pad into slidable contact with the outer surface of the polygon ring and the resultant force (average of Fh3 and Fh4) of outward radial forces received by the inside flat surface of the polygon ring around the halfway of the pad, whereby the couple can be formed simply and easily by the fluid pressure.

Description

Description Rotary fluid energy converter Technical field

The present invention relates to a rotary-type fluid energy conversion device used as a hydrostatic type fluid pump or motor. Background art

The inventor of the present invention first described a rotary fluid energy converter (

This energy converter has a pressure pocket (static pressure) for each cylinder on the outer periphery of the torque ring (corresponding to a polygon ring). By providing a couple on each side of the polygon ring by providing a bearing, the load on the supporting bearing of the torque ring is reduced.

In conventional rotary fluid energy converters, pressure pockets (hydrostatic bearings) are provided for each cylinder on the outer surface of the polygon ring, so that a large number of hydrostatic bearings are required. There were problems such as high leakage loss and complicated processing. Disclosure of the invention

In the present invention, the above disadvantages are improved, the leakage loss of the hydrostatic bearing is reduced while taking advantage of the features of the couple type, and machining is simple. SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides an easy-to-use rotary fluid energy converter, in which each inner plane of a polygon ring receives an outwardly directed pressure caused by a pressure in each cylinder. The radial forces are grouped into two groups, the radial force by the inflow-side cylinder and the radial force by the outflow-side cylinder, and each of them is configured to cancel the radial load collectively. It is a thing.

Specifically, in the rotary fluid energy converter of the present invention, as shown in FIG. 1, the outer peripheral surface of the polygon ring 4 is finished to a spherical smooth surface, and the cup is turned down. The pad-shaped static pressure pad 6 is movably held toward the center of the spherical surface by the pad holder 17 and is lightly pressed against the outer periphery of the polygon ring by a panel force.

The pad holder is held by casing at a position where the axis of the pad holder is perpendicular to the direction of the eccentricity of the spindle and the direction of the rotation axis, and passes through the rotation axis, and the pad holder of the cylinder block is mounted on the pad holder. A port pressure leading to the cylinder on the side half is introduced.

The static pressure pad fits into the inner diameter of the pad holder, but the cross-sectional area of the fitting diameter is determined by the force obtained by multiplying the area by the above port pressure, as in each side of the polygon ring. The static pressure pad side is selected so that it is equal to the resultant force of half of the inner surface. BRIEF DESCRIPTION OF THE FIGURES FIG. 1 is a cross-sectional view of a constant displacement hydraulic pump z-model using the present invention. FIG. 2 is a sectional view of a variable displacement hydraulic pump / motor using the present invention. FIG. 3 is an explanatory view of the operation-effect of the hydrostatic pad according to a cross-sectional view perpendicular to the axis of the apparatus of FIG. FIG. 4 is a graph showing the effect of the static pressure pad described in FIG. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the invention will be described based on examples with reference to the drawings.

Fig. 2 shows an embodiment in which the present invention is applied to a variable pump / motor having 7 cylinders. In this case, the pindle 1 is guided by a trapezoidal groove provided in the rear case 10 and can be moved in a direction perpendicular to the plane of the paper to change the amount of eccentricity. The fitting part with the hook is a taper. Accordingly, the center axis of the cylinder is substantially perpendicular to one surface of the taper, and the outward radial force applied to each side of the inner surface of the polygon ring 5 is inclined toward the shaft end of the input / output shaft.

Since the number of cylinders is 7, the force vector shown by Fh 3 indicates the resultant force of the outward radial forces applied to the three sides of the polygon ring halfway, and the force shown by Fh 4 The vector indicates the resultant force of the outward radial forces on the four sides of the ring. Therefore, the component force in the radial direction of Fh 3 and Fh 4 is equal, but the component force in the shaft end direction is 3 to 4.

The outer peripheral surface of the polygon ring 4 is finished to a spherical smooth surface The static pressure pad 6 with the cup facing down (the pad holder is unnecessary due to its structure) is held in the center of the spherical surface by the holding hole 71 provided in the front case 5. It is held movably and lightly pressed against the outer circumference of the polygon ring by the spring force. Then, a port pressure is introduced into the static pressure pad, which communicates with the cylinder on the half circumference of the cylinder block on the static pressure pad side.

The static pressure pad fits into the inside diameter of the holding hole provided in the front case.The direction and inside diameter of the holding hole is determined by the force obtained by multiplying the area of the holding hole by the above port pressure. It is chosen to be equal to the average of the inverse vectors of Fh 3 and Fh4 (shown as F).

The embodiment of FIG. 1 will be described with reference to FIG. 3 to explain the effect of reducing the bearing load by the hydrostatic pad.

As shown in Fig. 3, the direction of the force F that pushes the polygon ring back toward its center by the static pressure pad is constant (horizontal). The direction of the resultant radial radial force applied to each side of the inner surface fluctuates as the polygon ring rotates.

In other words, in FIG. 3 showing the case where the number of cylinders Z is nine, in the case of rotating in the direction of the arrow and pumping, the discharge port is kept until the seal bush 13 comes to the position shown in the figure. Since the pressure of 11 is applied, the five seal bushs 13, 23, 33, 43, 43, and 53 have high pressure, and the direction of the resultant force of the outward radial force is (Upward by 10 degrees, shown by Fu). However, Immediately after rotating from the position, the direction of the resultant force of the outward radial force changes suddenly because the seal bush 13 is connected to the suction port and the pressure is low, and the direction between the seal bush 33 and 43 is intermediate ( 10 degrees downward, indicated by F d). However, the magnitude of the resultant force does not change.

At this rotational position, the direction of the resultant force of the outward radial force (shown as Fd) is inclined most downward, so that the couple load constitutes a direction in which the bearing load of the polygon ring is completely canceled. The error vector (shown by Fr) with respect to (shown by Fh) is the largest, and this remains as the radial load of the polygon ring bearing.

Until the phase force reaches the phase further rotated by 10 degrees, the error cancels out by reducing the load as the direction of the resultant force approaches horizontal, and the outward force at the phase rotated by 10 degrees The direction of the resultant force of the radial force is horizontal (shown by Fh), and the force F that pushes the polygon ring toward its center by the static pressure pad is opposite to the force F, so it is a perfect couple. The bearing load of the polygon ring is canceled and becomes zero. When the phase is further rotated from this phase, the load cancellation residual Fr increases as the direction of the resultant force deviates from horizontal, and reaches the maximum value at a position rotated by 20 degrees.

The above-mentioned Fr, that is, the radial load for a half circumference is collectively canceled by one static pressure pad so that the remaining radial load (applied to the polygon ring bearing), the rotation angle, Fig. 4 shows the relationship between The loading weight of the polygon ring shaft (F = Fd = Fh = Fu) without the static pressure pad is also shown for comparison.

As shown in the upper part of Fig. 3, the maximum tilt angle α of the resultant force of the outward radial force is given by

Q! = 90 ° / Z

(Fr) max = 2 * sin (α / 2) * F

Power,

[Fr] max = 2 * sin (45 ° Z Z) * F

Z = 9

[Fr] max = 2 * sin 5 ° * F = 0.1743 * F = F / 5.74

[Fr] mean = [Fr] max / 2 = 0.0872 * F = F / 11.47 Z = 7

(Fr) max = 2 * sin (45 ° / 7) * F) = 0.224 * F = F / 4.47 (Fr) mean = [Fr] max / 2 = 0.112 * F = F / 8.93 That is, static pressure pad As a result, the polygon ring bearing load is reduced to 1 / 11.47 and 1 Z 8.93, respectively, on average.

The life of a ball bearing is inversely proportional to the cube of the load, and is a fluctuating load as shown in the figure.If calculated by integral calculation, the rate of increase in the calculated life of the ball bearing due to the hydrostatic pad Is 4300 times when Z = 9 and 1600 times when Z = 7. Industrial applicability

While utilizing the features of the couple type, it is possible to reduce the leakage loss of the hydrostatic bearing and to realize a rotary type fluid energy converter that is easy to process.

Claims

Claims: A cylinder block that engages with a spindle and radially forms a plurality of cylinders, and a cylinder block that fits into each cylinder of the cylinder block and that is outside the cylinder block. The end face is a flat seal bushing, the polygon ring is such that the seal bushing end face is in close contact with the inner flat surface, and the casing supports the bottle and covers the polygon ring. The polygon ring consists of a ring and a polygon ring. The fluid ring is rotatably supported around its central axis. The fluid energy converter has a pin ring outside the polygon ring. Provide a static pressure pad that is held by a casing at a position perpendicular to the direction of the eccentricity of the torque and slide the static pressure pad against the outer surface of the polygon ring. As a result, the inner surface on the pad side half circumference of the polygon ring is A rotary fluid energy converter characterized by forming a resultant force and a couple of outward radial forces, and almost canceling the bearing load of the polygon ring.