JP2001525511A - Pendulum piston motor - Google Patents

Abstract

(57) [Summary] Including a cylindrical housing (1) having a cylindrical (toroidal) orbital ring (2) therein, a pendulum piston (3) capable of swinging in two opposing swinging directions, and having a cylindrical shape. The race (2) is, at one point, divided by a piston chamber wall (4) which defines piston chambers (5 and 6) on both sides of the piston (3), and the pendulum piston (3) has a fly mass (10). ) Connected to the central output shaft (13) and configured to operate over an operating angle in each swinging direction of 340 ° to 355 ° or a hydraulically or pneumatically operated pendulum piston motor or ring ( Toroid) motor. The pendulum piston motor has two freewheel couplings (14, 15) acting in opposite directions, and also reverses the direction of rotation of the output shaft (13) during one swing direction movement of the pendulum piston (3). (17-21).

Description

DETAILED DESCRIPTION OF THE INVENTION

The present invention relates to a hydraulic or pneumatically operated pendulum piston motor or toroid piston motor.

This motor is a motor having a piston having a central output shaft which can reciprocate in a cylindrical (toroidal) chamber. The piston is configured to perform reciprocating work by the action of a hydraulic medium such as oil, water, or another liquid, or an air medium such as air, another gas, steam, or combustion gas. The pressure medium is alternately introduced into the opposing pressure chambers of the motor, so that the piston performs a reciprocating pendulum movement.

A pendulum piston motor or annular piston (toroid) motor of this type is known, for example, from DE-O-1.750.601 and GB-P-2.239.053. The devices of these two patent publications provide a reciprocating (vibrating) motion of the output shaft suitable for certain applications, but such reciprocating motion is used as a driving means for applications requiring constant driving in the same direction. It can be said that it is difficult to do. Therefore, the motor is not suitable as a drive motor for a rotating machine, a vehicle, or another device in which rotation in a certain direction or a drive motion having a substantially constant drive force constant is desired.

[0004] A further rotary actuator is known from GB-A-2.312.248. The rotary actuator includes a piston assembly that moves within an annular pressure chamber and provides angular movement of the drive shaft on a flange plate connected to the drive shaft by a ratchet-type clutch. The actuator is configured to convert a pressure signal into angular motion and operates based on the pressure signal.

[0005] None of the known prior art devices can provide unidirectional uniform rotation of the output shaft using a reciprocating pendulum piston motor. Therefore, it is a primary object of the present invention to provide a pendulum piston of the type described above which has a controllable and constant or nearly constant driving force despite the fact that the output shaft rotates in the same direction and the piston performs a reciprocating pendulum movement. It is to solve the problem of providing a motor.

[0006] Motors of the type described above offer several advantages. In other words, compared to conventional Otto engines, diesel engines, Wankel engines, and other types of internal combustion engines, it can be manufactured as a small and lightweight unit, and the driving force of the motor can be easily adapted to actual requirements, It can be driven by many different types of hydraulic or pneumatic media, offers very high efficiency relative to its weight, provides virtually constant driving power over the entire operating stroke, and emits no exhaust gas Alternatively, it can be driven by a pressure medium that does not provide other adverse environmental effects, and can be manufactured at substantially reduced cost for the motor effect. A further advantage of this motor is that during each single cycle of operation the motor produces much more work than a conventional internal combustion engine can generate per work cycle. That is, six to ten times the amount of work that the conventional four-stroke type internal combustion engine generates per operation cycle,
Alternatively, it is at least four times larger than the work that can be generated by a two-stroke type internal combustion engine.

FIG. 1 of the accompanying drawings shows the known principle of an internal combustion engine having a reciprocating piston and a rotating crankshaft having an output shaft. From such engines, a force is generated according to a kind of Gaussian curve, which is 0 for a two-stroke engine.
°, gradually increasing from 360 ° for a four-stroke engine, the maximum force on the output shaft is obtained at 90 ° and 450 °, respectively. Thereafter, the force gradually decreases until the force becomes zero at or near the next 180 ° and 540 °, respectively.

A pendulum piston motor can be designed to provide full force during substantially full pendulum movement in each of two opposing directions. The output is limited by means for supplying the hydraulic or pneumatic medium and reversing the direction of supply, but this means can be limited to 10-20 ° of its full revolution. . The pendulum motor is schematically illustrated in FIG.

In FIG. 3, the output of the pendulum piston motor is indicated by phantom lines, and the output of a four-stroke engine similar to a Gaussian curve is indicated by a double hatched portion between 360 ° and 540 °. ing. FIG. 4, which shows two full revolutions of the engine, shows the output of the pendulum piston motor and the two-stroke internal combustion engine correspondingly for two full revolutions of the engine, respectively. The average work performed by the four-stroke internal combustion engine is only about 1/8 of the work performed by the pendulum piston motor during the same operation period, and the average work performed by the two-stroke internal combustion engine is determined by the fact that the pendulum piston motor has the output shaft. It can be seen that this is only about one-fourth of the work performed during the period corresponding to two revolutions.

As described above, a normal pendulum piston motor provides a reciprocating or oscillating (oscillating) motion of an output shaft, the motion of which is special when a driving force having a certain direction of rotation is desired. It cannot be used as a driving force without complicated treatment. Therefore, according to the present invention, the pendulum piston motor comprises means for reversing the direction of rotation of the output shaft during either clockwise or counterclockwise movement of the pendulum piston. This is done by forming the motor with a planetary gear that reverses the direction of rotation in one of the stages of movement of the pendulum piston. In order to be able to receive power in both rotational directions, the pendulum motor further comprises two freewheel couplings, a first freewheel coupling for "forward" movement and a "freewheel coupling".
Second freewheel coupling for "backward" movement. The two freewheel couplings are mounted in opposing directions of movement to allow opposing rotational drive and freewheel travel, whereby the output shaft is driven in a constant rotational direction. Preferably, the planetary gears have a 1: 1 shift, but other gears can be used for the planetary gears to provide special effects, in which case the drive motion of the output shaft will be reduced. Periodic fluctuations are obtained.

[0011] The two freewheel couplings anticipate the rotational movement of the output shaft even with very small movements of the pendulum piston, and the two reaction freewheel couplings including the planetary gears eliminate the rotational movement of the output shaft. A step reversal is obtained.

The interaction between the two freewheel couplings and the planetary gears automatically provides the freewheel function of the output shaft. This means that idling is always obtained when the device that is drivingly connected to the output shaft runs faster than the drive motor. When the drive shaft of the pendulum piston motor is stationary, the device that is drivingly connected thereto can only move according to the clockwise direction of the pendulum piston motor. Therefore, the device of the present invention cannot involve any braking movement in the device.

The present invention will now be described in more detail with reference to the accompanying drawings. In the accompanying drawings, FIG. 1 schematically illustrates an Otto-type or diesel-type internal combustion engine as described above. FIG. 2 schematically illustrates the operation of the pendulum piston motor. FIG.
Describes a pendulum piston motor (virtual line area) and a four-stroke internal combustion engine (
FIG. 4 shows the amount of work performed by the pendulum piston motor and the two-stroke internal combustion engine in a corresponding manner. FIG. 5 shows a cross-sectional view of a simple type pendulum piston motor according to the invention in the plane of its output shaft, and FIG. 6 is a cross-sectional view along the line VI-VI in FIG. FIG. 7 is a diagram schematically showing the operation of the pendulum piston motor according to the present invention when viewed from a direction perpendicular to the output shaft. FIG. 8 shows the combined pendulum piston motor in a manner similar to FIG. FIG. 9 shows in more detail an example of a control device for alternately supplying the pressure medium to the two piston chambers of the pendulum motor,
0 details the position of the control device for the introduction of pressure medium into the piston chamber on the left-hand side of the figure after readjustment of the control device.

The pendulum piston motor according to the invention shown in FIGS. 5 to 7 generally comprises a cylindrical housing 1 having an annular (toroidal) cylindrical race 2. In the cylindrical bearing ring 2, the pendulum piston 3 is arranged to reciprocate between two sides of the piston chamber wall 4. The piston chamber wall 4 has means for supplying pressure medium to piston chambers 5 and 6 formed on both sides of the pendulum piston 3.

The cylindrical housing 1 consists of two half-housings 7 and 8 divided perpendicular to the output shaft. The half-housings 7 and 8 are sealed, as known in the prior art, both outside and inside 9 with respect to the cylindrical race 2, forming two opposed piston chambers 5 and 6 sealed together. I do. The pendulum piston 3 is formed as a projection with an inner fly mass 10 having a piston neck 10a that keeps the piston 3 in position within the cylindrical race 2. The fly mass 10 is mounted in the center of the cylindrical housing by bearings 11 and 12 on both sides of the cylindrical housing and in cooperation with a rotating shaft 13 and two reaction freewheel couplings 14 and 15. One freewheel coupling 14 provides drive transmission in one direction, indicated by arrow 16, and provides a freewheel function in the reverse rotation direction. Also, the other freewheel coupling 15 provides drive transmission in the opposite direction compared to the freewheel coupling 14, as indicated by arrow 17. In the two opposing directions of the freewheel coupling, a substantially resistive rotational movement is obtained, which is known per se. Right freewheel coupling 15 shown in FIG.
Are enclosed in the inner sun wheel 18 of the planet gear. The outer sun wheel 19 of the planetary gear is fixedly mounted on the axially projecting flange 20 of the fly mass 10. The outer sun wheel 19 is connected to the inner sun wheel 1 by three or more planet wheels 21.
8 for drive connection. In order to provide uniform movement in both rotational directions, the planet gears must have a 1: 1 shift between the planet wheel 21 and the inner sun wheel. However, for special applications, it is also possible to use other transmissions, so that the piston moves faster or slower in one piston movement direction than in the opposite direction.

The purpose of the planetary gear is to reverse the direction of rotation during the piston movement to one side and
3 is always driven in the same rotational direction.

A supply means for the hydraulic or pneumatic medium is connected to the piston chamber wall 4.
This supply means can be formed in various ways, but is arranged and adjusted by the geometry of the movement of the pendulum piston to alternate the supply of pressure medium between the two piston chambers 5 and 6 at the desired position of the piston 3. You have to do it.
For optimum work, the pressure supply alternation can take place when the piston has reached the rear piston chamber wall or when it is very close to said wall. FIG. 7 shows that the pressure medium supply can be regulated by means of a rotatable valve 22 whose movement can be controlled by the movement of the piston 3, so that the pressure medium supply is alternated between both chambers 5 and 6. It is shown. The operation and control of the valve can be effected mechanically, electronically, hydrodynamically or by other means in response to the movement of the piston 3 in the cylindrical race 2.

FIG. 7 shows that a pressure medium is supplied to the piston chamber 5, thereby causing the piston 3 to rotate clockwise. Inactive piston chamber,
In FIG. 7, in order to discharge the hydraulic or pneumatic medium from the chamber 6, the device comprises:
Any known type of discharge means not shown, such as a passage in the piston chamber wall 4 having a non-return valve to the outside air, is formed. Such a check valve will only function when the opposing piston chamber is under pressure. In FIG. 7, the piston medium 5 providing clockwise movement receives pressure medium from a passage 24 in the piston chamber wall, whereas the opposite medium chamber 6 discharges pressure medium.

The pressure supply can be varied as desired to provide the required torque and rotational speed at output shaft 13. The device can be formed with a choke valve connected to a pressure medium supply means to provide a gentle start, a controlled speed and a controlled torque.

A pendulum piston motor of the type described above can be used for many different applications. For example, since the force and speed at the output shaft 13 can be changed from zero to the maximum simply by controlling the pressure of the drive pressure medium, the drive motor can be used for all types of vehicles and machines without using a transmission. Can be used as Also, there is no need for a slip clutch to provide a gentle start, since a gentle start can be easily achieved with a choke valve that controls the pressure and flow of fluid into the cylindrical chamber from zero to maximum. The freewheeling of the vehicle consists of two freewheel couplings 14
And 15 are obtained. The rear drive function can be obtained by using a simple mechanical reversing device.

FIGS. 9 and 10 show a device in which the supply of pressure medium between the two pressure chambers 5 and 6 is switched by the piston 3 itself. In this case, the pressure altering piston is formed as a rotatable slide 25 with an operating arm 26 which is provided on both sides of the piston chamber wall 4 so as to project downward. The working arm 26 is pushed by the piston 3 when it reaches the end of its working stroke, so that the slide valve is switched from clockwise movement of the piston to counterclockwise movement. Also,
The reverse is also true. The pressure medium is supplied from the central bore 27 via the passages 28 and 29 and the openings 30 and 31 of the valve slide 25 and from there further through the passages into one of the piston chambers 5 and 6. In FIG. 9, the valve slide 25 is shown in a neutral position where no pressure medium is supplied. In FIG. 10, the piston 3 makes a clockwise stroke and presses on the arm 26, so that the valve slide 25 is in a position where the pressure medium is introduced into the counterclockwise piston chamber 26 via the passage 29 and the opening 31 of the valve slide 25. , Whereby the piston 3 has started its counterclockwise stroke.

Since the planetary gears 17-21 reverse the rotation direction of the outer sun wheel 19 in one stroke of the motor, the output shaft 13 always rotates in the same direction. this is,
Enabled by the action of the two opposing freewheel couplings 14 and 15.

The pendulum piston motor described above can operate over a rotation of up to 340-350 °. Estimating in one complete working cycle, corresponding to two revolutions of the crankshaft of an Otto or diesel internal combustion engine, the full effect already occurs from the moment when the pressure medium is supplied to the pressure chamber 5 for clockwise rotation. As a result, the full effect is exerted from about 5 ° to 355 °, and then the supply of the pressure medium is switched to the introduction into the pressure chamber 6, and the full effect is exerted from about 365 ° to 715 °, as shown in FIGS. 4 can be seen from the schematic curves. In addition, 4
It is also evident that the stroke engine performs only one-eighth of the work of the pendulum piston motor on average, and the two-stroke engine performs less than one-fourth of the work of the pendulum motor. It is.

As regards the alternation of the pressure medium supply between the pressure chambers 5 and 6, a slight interruption of operation appears corresponding to 10-20 ° of the total work of one full revolution cycle. This minor work interruption is usually equalized by the fly mass 10 of the pendulum piston motor. The fly mass 10 must be braked and stopped before pressurized fluid is introduced into the opposing pressure chamber and the motor is operated in the opposite direction.

When the valve switches the supply of pressure medium from one pressure chamber to the other, the outlet of the pressure medium in the inactive pressure chamber is turned on before the pressure fluid is introduced into said pressure chamber and activated. Must be closed. This means that the pressure fluid trapped in the inert pressure chamber will be in a compressed state if air is used as the pressure fluid. Following this compression of the trapped air, the piston is braked and gently stopped at the end of the stroke. Compressed air can be exhausted using a pressure control valve that opens at a relatively high pressure, for example, 8 bar. Thus, the compressed air is introduced into the compressed air tank 34 (see FIG. 7) and is reused as a part of the driving pressure medium in the next driving stage.

However, such interruption of operation can be completely eliminated in practice, and as shown in FIG. 8, two or more motors are interconnected in series on the same output shaft 13 to equalize the operation characteristics of the motors. Can be In such a case, two or more motors rotate with respect to each other with respect to the drive shaft 13. That is, the piston chamber walls 4 of two or more motors rotate around the drive shaft, for example, 180 ° when using two coupled motors, 120 ° when using three coupled motors, and so on. Placed. As a result, the motors are operated in relation to each other, so that
Interruptions of operation corresponding to -5 ° cancel each other out. FIG. 8 shows that the pressure medium supply means 32 and 33, including the piston chamber walls, are rotated by 180 ° with respect to the output shaft.

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing an Otto-type or diesel-type internal combustion engine.

FIG. 2 is a schematic diagram showing the operation of a pendulum piston motor.

FIG. 3 is an output diagram of a curved pendulum piston motor showing the work done by both the pendulum piston motor (virtual line region) and the four-stroke internal combustion engine (double virtual line region) according to the present invention.

FIG. 4 is an output diagram correspondingly showing the amount of work performed by a pendulum piston motor and a two-stroke internal combustion engine.

FIG. 5 is a cross-sectional view of a simple type pendulum piston motor according to the present invention, as viewed in the plane of its output shaft.

FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 5;

FIG. 7 is a schematic view of the operation of the pendulum piston motor according to the present invention as viewed from a direction perpendicular to the output shaft.

FIG. 8 is a sectional view showing the combined pendulum piston motor in the same manner as in FIG. 5;

FIG. 9 is a diagram showing an example of a control device for alternately supplying a pressure medium to two piston chambers of a pendulum motor.

FIG. 10 shows the position of the control device for the introduction of pressure medium into the left piston chamber after readjustment of the control device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cylindrical housing 21 Planetary wheel 2 Cylindrical raceway ring 22 Rotatable valve 3 Pendulum piston 23 Discharge means 4 Piston chamber wall 24 Passage 5 Cylindrical chamber 25 Valve slide 6 Cylindrical chamber 26 Working arm 7 Semi-cylindrical housing 27 Center Drilling 8 Semi-cylindrical housing 28 Passage 9 Sealing 29 Passage 10 Fly mass 30 Drilling 10a Piston neck 31 Drilling 11 Bearing 32 Pressure supply means 12 Bearing 33 Pressure supply means 13 Rotating shaft 34 Pressure chamber 14 Freewheel coupling 15 Freewheel coupling 16 Arrow 17 Arrow 18 Inner sun wheel 19 Outer sun wheel 20 Tsuba

[Procedure for Amendment] Submission of translation of Article 19 Amendment of the Patent Cooperation Treaty

[Submission date] April 2, 1999 (1999.4.2)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Correction contents]

[Claims]

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Claims (10)

[Claims] A cylindrical housing (1) having a cylindrical (toroidal) orbital ring (2) therein, wherein a pendulum piston (3) is capable of reciprocating swinging in two opposing swinging directions. The race (2) is, at one point, divided by a piston chamber wall (4) defining piston chambers (5 and 6) on either side of the piston (3), and the pendulum piston (3) has a fly mass ( A hydraulic or pneumatically operated pendulum piston motor or toroid motor connected to the central output shaft (13) via 10) and operating over an operating angle in each swing direction of 340 ° to 355 °. , The pendulum piston motor has two freewheel couplings (14, 15) acting in opposite directions, and the pendulum piston (
Means (1) for reversing the rotation direction of the output shaft (13) during one swing direction movement of (3).
7-21), wherein the pendulum motor is formed. 2. The pendulum according to claim 1, wherein the means for reversing the direction of rotation of the output shaft (13) during one swinging movement of the pendulum piston (3) comprises a planetary gear. Piston motor. 3. An outer sun wheel (19) of a planetary gear comprises a pendulum piston (3).
And the inner sun wheel (17) of the planetary gear is connected to one of the freewheel couplings (14, 15).
3. The pendulum piston motor according to claim 2, wherein the pendulum piston motor is connected to the output shaft (13) of the motor via (5). 4. The pendulum piston (3) during driving of the planetary gear of the pendulum piston (3).
A pendulum piston motor according to claim 2 or 3, characterized in that the planetary gears have a 1: 1 shift to provide the same speed / power characteristics as during free counter-movement. 5. The piston is operated in a reciprocating manner by a hydraulic medium such as oil, water or other liquid, or by a pneumatic medium such as air or other gas, steam or combustion gas. A pendulum piston motor according to any of the preceding claims, wherein the piston is arranged to alternately supply a pressure medium into opposing pressure chambers (5, 6) of the motor such that the piston performs a reciprocating pendulum movement. Pressure change valve (
22; 25), wherein the pendulum piston motor is formed. 6. The function of a pressure diverter valve (22; 25) so as to alternate the pressure supply when the piston (3) is at or near one of the end positions of the piston chamber wall (4). 6. The pendulum piston motor according to claim 5, wherein the motor is controlled by the movement of a pendulum piston. 7. A rotatable slide (25) with an operating arm (26) extending into a piston chamber (5, 6) in a position which can be acted on by a piston (3) in each direction of movement. 7. The pendulum piston motor according to claim 5, wherein the function of the pressure-shift valve is readjusted. 8. 8. A control valve for controlling the flow of fluid to the piston chambers (5, 6) and the pressure of the hydraulic or pneumatic medium, thereby controlling the speed and torque of the output shaft (13). A pendulum piston motor according to any of the preceding claims, further comprising: 9. A pendulum piston motor according to claim 1, comprising two or more interconnected pendulum piston motor units acting on the same output shaft (13). 10. The pendulum piston motor according to claim 9, wherein the piston chamber walls of the two or more interconnected pendulum piston motor units are arranged offset from one another.