JPH0350297Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) This invention relates to a hydraulic motor that extracts torque by rotating the inner rotor of a trochoid gear using hydraulic pressure.

(Prior Art) The conventional hydraulic motor shown in FIG.
A valve plate 3 having an oil passage 2 formed therein is used.

Then, the inflow/outflow port 4 is communicated with the relay chamber 5, and another inflow/outflow port 6 is communicated with the relay chamber 7, and high pressure oil is supplied to either the inflow/outflow port depending on the rotational direction of the motor. However, low pressure oil is discharged from the other inflow and outflow port.

Then, the side surfaces of the valve body, that is, the relay chambers 5 and 7
The pressure action in the relay chamber 5 or 7 cancels out the thrust load that pushes the valve body 1 to the right in the drawing due to the pressure action on the opposite side.

(Problems to be Solved by the Present Invention) In the conventional hydraulic motor as described above, two relay chambers 5 and 7 are formed on one side of the valve body 1. The pressure receiving area inside cannot be made large enough. On the other hand, since the pressure receiving area on the surface opposite to the relay chambers 5 and 7 is almost the entire area of the valve body, the pressure action on both sides of the valve body becomes unbalanced.

As a result, the sliding resistance between the valve body 1 and the valve seat increases, resulting in severe wear between the two, and the increased sliding resistance also increases energy loss.

Further, in this conventional motor, the spring force of the spring 8 is applied to the valve body 1 in advance in anticipation of the valve body being worn out as described above.
Incorporating the spring 8 in this manner itself has the problem of complicating the structure and making the assembly work difficult.

The purpose of this invention is to provide a hydraulic motor that balances the acting forces on both sides of the valve body to make the valve body hydraulically float, thereby reducing energy loss due to wear of the valve body and its frictional resistance. be.

(Means for solving the problem) This invention provides a valve body that rotates integrally with the output shaft, and the rotation of this valve body switches between a high-pressure oil passage and a low-pressure oil passage, and the high-pressure oil is This is based on a hydraulic motor configured to act on the inner rotor of a trochoid gear to rotate the inner rotor and extract the torque.

Based on the above-described hydraulic motor, this invention separates the output shaft and the valve body, and connects them so that they rotate integrally with each other. Further, one side of the valve body is brought into rotatable contact with the body side, and the other side is brought into rotatable contact with the trochoid gear side, and the shape and pressure receiving area of both sides of the valve body are made equal. A plurality of oil passages parallel to the axis are formed in the circumferential direction of the valve body, and both ends of the oil passages are opened on both sides of the valve body. Furthermore, a first annular groove that constantly communicates with the first inflow/outflow port and a second annular groove that constantly communicates with the second inflow/outflow port are formed on the outer periphery of the valve body, and the plurality of oil passages are The first annular groove and the second annular groove are alternately communicated, and the pressure in the oil passage is applied to both sides of the valve body to equalize the acting force on both sides, and the valve body is hydraulically floated. It is configured to allow

(Operation of the present invention) As described above, since both ends of the plurality of oil passages parallel to the axis are opened on both sides of the valve body, high-pressure oil flowing into these oil passages acts on both sides of the valve body.

Furthermore, since the output shaft and the valve body are separate, the shapes of both side surfaces of the valve body are the same, and the areas thereof are approximately equal, the acting forces on both sides of the valve body are equal.

(Effects of the present invention) In this invention, since the valve body is hydraulically floated, wear due to friction of the valve body can be prevented.
Moreover, energy loss due to frictional resistance can be reduced.

Furthermore, since the output shaft and the valve body are separate, the pressure receiving areas on both sides of the valve body can be equalized. Therefore, even if high-pressure oil leaks to the side surface of the valve body, the pressure effect is equalized and the above-mentioned hydraulic floating state can be maintained.

(Embodiment of the present invention) A valve housing 11, a plate 12, a trochoid gear G, and a cover 13 are installed in order on one side of the body 10 of the embodiment of the present invention shown in FIGS. 1 to 7. , these are integrally fastened with bolts 14.

Note that the positions and phases of the body 10, valve housing 11, and plate 12 are adjusted by dowel pins 47 and 48.

The body 10 is provided with an output shaft 16, which is rotatably supported by a bearing 15 provided on the body 10. A recess 17 is formed at the inner end of the output shaft 16, and a spline 18 is formed within the recess 17.

The trochoid gear G is composed of a trochoid outer 19 and an inner rotor 20, and the number of teeth of the inner rotor 20 is one less than that of the trochoid outer 19, and a spline is formed in the center of the inner rotor 20. 21 is formed.

Then, the output shaft 16 and the inner rotor 20
Splines 23 and 24 are formed at both ends of the drive shaft 22 that connects the
4 is engaged with the spline 18 of the output shaft 16 and the spline 21 of the inner rotor 20.

Therefore, if the inner rotor 20 rotates while revolving around the trochoid outer 19,
The output shaft 16 will rotate.

A valve body V is rotatably housed in the housing 11 as described above, and as shown in FIGS. 1 and 7, a notch 25 formed in the valve body V has a
A convex portion 26 formed on the output shaft 16 is engaged with the valve body V so that the valve body V rotates together with the output shaft 16.

The valve body V configured as described above has one side surface in sliding contact with the plate 12 and the other side surface also in sliding contact with the body 10.

A plurality of oil passages 30 and 31 parallel to the axis are formed in this valve body V, and the oil passages 3
0 and 31 are opened on both sides of the valve body V. Furthermore, the openings of the oil passages 30 and 31 are aligned at a constant interval in the circumferential direction on both sides of the valve body V, as shown in FIGS. 4 and 5.

As is clear from FIG. 3, a plurality of communication holes 32 are formed in the plate 12 that contacts one side of the valve body V. Further, as shown in FIG. 2, a plurality of perforations 33 are formed in the body 10 that contacts the other side of the valve body V.
and the communication hole 32 have the same size and the same phase, so that the correspondence relationship between the two is completely matched. Then, on both sides of the valve body V, the dimensions of the parts on which pressure acts are made completely the same, so that the hydraulic pressure generated when the motor is operated acts the same on both sides of the valve body V, and the valve The body V can be maintained in a floating state.

Furthermore, a first annular groove 35 communicating with the first inflow/outflow port 34 and a second annular groove 37 communicating with the second inflow/outflow port 36 are formed on the outer periphery of the valve body V. Seals 38 to 40 are installed in seal grooves formed on both sides of the annular grooves 35 and 37 to prevent the annular grooves 35 and 37 from communicating with each other.

As shown in FIG. 4, the first annular groove 35 communicates with one group of oil passages 30, and as shown in FIG. 5, the second annular groove 37 communicates with the other group of oil passages 31.

When high-pressure oil is supplied from the first inflow and outflow port 34, the high-pressure oil passes through the first annular groove 35 → a predetermined oil passage 30 → the communication hole 32 of the plate 12, as shown in FIG. , trochoid outer 1
9 and the inner rotor 20, and the hydraulic oil in a chamber 42, which is separate from this chamber 41, is supplied from the communication hole 33 to the oil path 3.
1 → flows out from the second inflow/outflow port 36 via the second annular groove 37 .

When high pressure oil is supplied to the chamber 41 as described above, the inner rotor 20 rotates in the direction in which the volume of the chamber 41 expands, that is, in the direction of the arrow 43, and transmits the rotational force through the drive shaft 22. It is transmitted to the output shaft 16.

In the process of rotating the output shaft 16 in this way, high pressure oil is introduced into one of the oil passages 30, but since this oil passage 30 is open on both sides of the valve body V, the high pressure is Acts on both sides of V.

Since high pressure acts on both sides of the valve body V and the acting forces are equal, the valve body V becomes floating due to the hydraulic pressure, the frictional force of the valve body V decreases, and the energy loss is reduced. .

Further, in this embodiment, since the valve body V and the output shaft 16 are separate, the pressure receiving areas on both sides of the valve body V can be made completely equal. Therefore, even if high pressure leaks from the oil passage 30 or 31, the pressure balance will not collapse due to the action of the high pressure.
In particular, since the notch 25 and the protrusion 26 are used to connect the valve body V and the output shaft 16, pressure oil can penetrate between them. Therefore, even this notch 25 cannot become an element that disrupts the pressure balance.

If the output shaft and valve body are integrally formed,
There is a difference in the pressure receiving area on both sides of the valve body by the cross-sectional area of the output shaft. Therefore, if high-pressure oil leaks as described above, an imbalance will occur depending on the difference in the pressure-receiving areas. However, according to this embodiment, such problems do not occur at all.

Note that the reference numerals 27 and 2 shown in FIGS. 1 and 3
Reference numeral 8 denotes a ball check valve which, when the pressure on the body 10 side exceeds the tank pressure, causes the pressure oil to flow out from the first or second inflow/outflow port communicating with the tank.

Further, reference numerals 44 and 45 are pins for preventing the ball check valve 44 from falling off.

The reason why a pair of ball check valves is provided in this way is that the annular groove on the low pressure side differs depending on the direction of rotation of the motor.

[Brief explanation of drawings]

Figures 1 to 7 show an embodiment of this invention, in which Figure 1 is a sectional view, Figure 2 is a scaled sectional view taken along the - line in Figure 1, and Figure 3 is a cross-sectional view taken along the - line in Figure 1. Figure 4 is a cross-sectional view of the valve body taken in a direction perpendicular to the axis and along the first annular groove, and Figure 5 is a cross-sectional view of the valve body taken in the direction perpendicular to the axis and along the second annular groove. Figure 6 is an operation explanatory diagram showing the relationship between the trochoid gear and the valve body, Figure 7 is a front view with the output shaft and valve body separated, and Figure 8 is a cross-sectional view of the conventional It is a diagram. G... Trochoid gear, 16... Output shaft, 19
... Trochoid outer, 20 ... Inner rotor, V ... Valve body, 30, 31 ... Oil path, 34 ...
First inflow/outflow port, 35... First annular groove, 36...
...Second inflow and outflow port, 37...Second annular groove.

Claims (1)

[Scope of utility model registration request] A valve body that rotates integrally with the output shaft is provided, and the rotation of this valve body switches between a high-pressure oil passage and a low-pressure oil passage, and the high-pressure oil acts on the inner rotor of the trochoid gear to In a hydraulic motor configured to rotate a rotor and extract its torque, the output shaft and the valve body are separate, and the two are connected so that they rotate integrally with each other, and one side of the valve body is The valve body is rotatably contacted with the body side, and the other side is rotatably contacted with the trochoid gear side, and the shape and pressure receiving area on both sides of the valve body are made equal, while an oil passage parallel to the axis is connected to the valve body. A plurality of oil passages are formed in the circumferential direction, and both ends of the oil passages are opened on both sides of the valve body, and furthermore, a first annular groove that constantly communicates with the first inflow/outflow port and a second outflow port are formed on the outer periphery of the valve body. A second annular groove is formed that constantly communicates with the inlet port, and the first annular groove and the second annular groove are alternately communicated with the plurality of oil passages, and the pressure in the oil passage is distributed to both sides of the valve body. A hydraulic motor configured to equalize the acting force on both sides of the valve body and to hydraulically float the valve body.