JPH0711272B2 - Liquid Sho agency - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a rotary hydraulic engine used as a static pressure type fluid pump or a fluid motor.

[Conventional technology]

This type of conventional rotary hydraulic engine, that is, a static pressure type rotary fluid pump / motor, converts the rotational force of the input shaft into a linear force of a piston or a plunger, or converts the linear force of a piston into an output shaft. A mechanism such as a cam mechanism or a link mechanism for converting into the rotational force of is adopted. Therefore, in such a product, a strong pressing force or twisting force will act between the components, so that bearing parts, balls, rollers, etc. that depend on the wedge action of the oil film due to the oiliness and viscosity of the lubricating oil The existence of bearings that depend on the rolling action is essential. Therefore, it is necessary to use oil or the like having an appropriate viscosity as the working fluid. That is, it is difficult to perform smooth operation with water or a working fluid having a viscosity close to that, and the life of the equipment is extremely short. Therefore, the type of working fluid that can be used is limited. is there. Further, in the case where a rolling bearing is used, it is difficult to improve the durability because the fatigue life of the bearing affects the life of the entire equipment, and since the rolling bearing is relatively bulky, the equipment can be made compact or lightweight. There is also a problem that it is difficult to realize. Therefore, a "rotating fluid energy converter" (Japanese Patent Laid-Open No. 58-77179) has been proposed as an invention for solving such a problem.

However, in the previously proposed invention, since the torque generating part due to the static pressure of the liquid is located on the outer peripheral side in the engine, it is inevitable that the size of the entire engine is increased and the piston and the torque ring slide. There is a problem that the range becomes large and the heat generated by friction also becomes large.

[Problems to be solved by the invention]

The present invention is based on the existence of a mechanical power conversion mechanism for converting a rotational force of an input shaft into a linear actuating force of a piston or the like, or converting a linear actuating force of a piston or the like into a rotational power of an output shaft. It is an object of the present invention to fundamentally solve the problems that occur and to provide a practical hydraulic engine in which the size of the entire engine is reduced and heat generation is minimized.

[Means for solving problems]

In order to achieve such an object, the present invention eliminates a mechanical power conversion mechanism and can directly generate a couple force corresponding to an input / output torque in a torque ring fitted on a pintle by a static pressure of hydraulic fluid. It is characterized in that it is configured as follows.

That is, a pintle that is eccentrically disposed with respect to the engine axis and a plurality of inner static pressure bearing mechanisms that are equidistantly arranged in the circumferential direction are externally fitted to the pintle and the inner sides of the outer periphery of the pintle. A torque ring having a piston sliding surface formed at a portion corresponding to the hydrostatic bearing mechanism, and an outer periphery of the torque ring concentric with the engine axis and rotatably disposed in the engine housing. A cylinder ring having a cylinder hole at a portion facing the piston sliding surface, and a slidably inserted into each cylinder hole of the cylinder ring so that each tip of the cylinder ring is outside the piston sliding surface on the outer circumference of the torque ring. A plurality of pistons engaged through a hydrostatic bearing mechanism and a supply / discharge system passage for supplying / discharging hydraulic fluid to / from a hydraulic pressure passage formed in a torque ring so as to connect the inner and outer hydrostatic bearing mechanisms to each other are provided. Ingredient And, characterized by being configured so as to generate torque in the torque ring by the sum of the couple of the hydraulic static pressure when the hydraulic pressure in the inner and outer side hydrostatic bearing mechanism is introduced.

[Operation] According to such a configuration, when used as a motor, first, by supplying high-pressure hydraulic fluid to one supply / discharge path and connecting the other supply / discharge path to the tank, Rotational torque can be generated in the torque ring, and the torque ring and the cylinder ring rotate synchronously. That is, in this case, the volume of the liquid chamber passing through one region corresponding to the one supply / discharge path gradually increases with the rotation of the torque ring, and the liquid chamber passing through the other region. , Its volume gradually decreases. Then, a couple of force is generated in the torque ring by the static pressure of the high-pressure hydraulic fluid introduced into the inner static pressure bearing mechanism and the outer static pressure bearing mechanism which communicate with the liquid chamber passing through the one region. Then, this couple causes the torque ring to rotate.

When used as a pump, the torque ring is rotationally driven by an external force. As a result, the volume of the liquid chamber passing through one of the regions gradually decreases as the torque ring rotates, and the volume of the liquid chamber passing the other region gradually rotates with the rotation of the cylinder ring. Its volume gradually increases. Therefore, the hydraulic fluid sucked from the other supply / discharge system path corresponding to the other area is pressurized in the one area and discharged from the supply / discharge system path corresponding to the one area. Then, due to the static pressure of the high-pressure hydraulic fluid introduced into the inner static pressure receiving mechanism and the outer static pressure bearing mechanism communicating with the liquid chamber passing through the one region, a couple force is generated in the torque ring. ， This couple balances with the external force applied to the torque ring. Since this couple generating portion is located inside the engine, the sliding range between the torque ring and the piston for generating couple is also small.

〔Example〕

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

FIG. 1 is a half sectional view of a hydraulic engine according to the present invention,
FIG. 2 is a sectional view taken along the line II-II in FIG.
As shown in these drawings, in this hydraulic engine, a pintle 1 is arranged so that its shaft center can be displaced with respect to an engine shaft center portion m. That is, a recess having a diameter larger than the diameter of the pintle is formed in the center of the back wall 2a of the housing 2, and the pintle 1 is supported in the recess so that it can be displaced vertically. 2A is a dovetail groove type slide mechanism formed on the right end surface of the pintle 1. A capacity adjusting mechanism 21 for adjusting the amount of eccentricity d with respect to the engine axis m is provided on the back wall 2a of the housing 2. The capacity adjusting mechanism 21 has a feed screw 22 arranged in parallel with the back wall 2a in a state where movement in the axial direction is prohibited,
The screw 22 is screwed into the pintle 1. 23 is this back wall
It is a hole formed in 2a. Further, the adjusting mechanism 21 is provided with a stepping motor 25 for rotating the feed screw 22 through a speed reducing mechanism 24 to move the pintle 1 forward and backward, but the stepping motor 25 is appropriately rotated in forward and reverse directions. Thus, the amount of eccentricity of the pintle 1 with respect to the engine axis m can be adjusted to a desired value including zero. In the illustrated state, the shaft center n of the pintle 1 is displaced from the shaft center m of the engine by a displacement amount d. A torque ring 5 is rotatably fitted on the pintle 1 via a plurality of inward static pressure bearing mechanisms 4 provided at equal intervals in the circumferential direction.

The torque ring 5 has a polygonal columnar shape in which a flat piston sliding portion 6 is formed on a portion of the outer periphery thereof corresponding to each of the inward static pressure bearing mechanisms 4, and one end side thereof is located outside the housing 2. It is configured to be transmitted to the extending input / output shaft 7. That is, a concave portion is provided at the left end of the torque ring 5 and the internal teeth 5S are formed inside thereof. On the other hand, inner teeth 7S are similarly formed on the right end of the input / output shaft 7. Three
Is a transmission shaft having gears 10 and 16 meshing with both teeth 5S and 7S at both ends. This is because in such a transmission mechanism, the torque ring 5 is eccentric with respect to the engine axis m like the pintle 1. Further, the inner static pressure bearing mechanism 4 is configured such that a pressure pocket 8 is formed on the inner periphery of the torque ring 5 and a pressure liquid can be introduced into the pressure pocket 8. A cylinder ring 9 concentric with the engine axis m and rotatable in the housing 2 is provided around the outer circumference of the torque ring 5.
Are arranged in a loosely fitted state. This cylinder ring 9
It is of a thick-walled cylindrical shape, and has cylinder holes 11 opened at the portions facing the piston sliding surfaces 6, respectively. Then, the pistons 12 are slidably fitted in the respective cylinder holes 11, and the tip end surfaces 12a of the respective pistons 12 are fitted to the corresponding piston sliding surfaces 6 through the outer hydrostatic bearing mechanism 13.
I am in contact with. The outer static pressure bearing mechanism 13 is configured such that a pressure pocket 14 is formed on the tip end surface 12a of the piston 12 and a pressure liquid can be introduced into the pressure pocket 14. The torque ring 5 and the cylinder ring 9
And are connected via an Oldham's shaft coupling 15 so that they can rotate synchronously. The cylinder ring 9 is rotatably fitted to the housing 2 via a plurality of third hydrostatic bearing mechanisms 17. The third hydrostatic bearing mechanism 17 has a pressure pocket 18 formed on the outer periphery of the cylinder ring 5 so that a pressurized liquid can be introduced into the pressure pocket 18. By changing the eccentric amount of the pintle 1 by the capacity adjusting mechanism 21, the capacity of the pump or the motor is changed. That is, in the cylinder hole 11 of the cylinder ring 9, there is formed a liquid chamber 26 whose volume is increased or decreased by the projecting and retracting operation of each piston 12 accompanied by the synchronous rotation of the torque ring 5 and the cylinder ring 9. By changing the amount of eccentricity, the volume increase / decrease amount of each liquid chamber 26 per cycle is changed.

The liquid chambers 26 and the corresponding hydrostatic bearing mechanisms 4,
In addition to providing a hydraulic pressure communication path 27 that communicates with 13, 17, a pair of supply / discharge system paths 28, 29 are provided in the pintle 1.
The supply / discharge system passages 28, 29 are taken out to the outside through a through hole 2K formed in the back wall 2a of the housing 2. The through hole K is formed large so that the pintle 1 can be displaced. The hydraulic pressure passage 27 is formed in the torque ring 5 and connects the inner static pressure bearing mechanism 4 and the outer static pressure bearing mechanism 13 to each other.
The port 31, a second port 32 bored in the axial center portion of the piston 12 to communicate the outer static pressure bearing mechanism 13 and the liquid chamber 26, and the liquid chamber 26 bored in the cylinder ring 9. And a third port 33 for communicating the third hydrostatic bearing mechanism 17 with each other.
It consists of and. Further, one of the supply / discharge system passages 28 has an engine axis, that is, the axis m of the cylinder ring 9 and
It is for supplying and discharging the working liquid to and from the liquid chamber 26 passing through the region A existing on the right side in FIG. 2 of the virtual dividing plane Q including the axis n of It comprises a trunk port 34 and a plurality of branch ports 35 that open the trunk port 34 to the outer peripheral surface of the pintle 1. Also,
The other supply / discharge system path 29 is for supplying / discharging the working liquid to / from the liquid chamber 26 passing through the region B existing on the left side in FIG. The trunk port 36 provided inside and the trunk port 36 are used for the pintle 1
And a plurality of branch ports 37 opened on the outer peripheral surface of the.

Numerals 19 and 20 are bearings for supporting the input / output shaft 7 to the housing 2 in an auxiliary manner. Further, 38 indicates a fixture.

Next, the operation of this embodiment will be described.

First, when used as a hydraulic motor, high-pressure hydraulic fluid is supplied to the liquid chamber 26 existing in the first region A through the first supply / discharge system passage 28, for example. Then, the axis n of the pintle 1 is eccentric to the engine axis m by a required distance d as shown in the figure. Then, as shown in FIG. 3, in the first region A, the action line of the force Fa acting on the torque ring 5 by the static pressure of the hydraulic fluid introduced into the pressure pocket 8 of the inner static pressure bearing mechanism 4 becomes Due to the static pressure of the fluid introduced into the corresponding pressure pocket 14 of the outer static pressure bearing mechanism 13, the force Fb acting on the torque ring 5 is deviated from the line of action, and the forces Fa and Fb And are two forces of equal magnitude, opposite directions, and parallel to each other, that is, a couple.
Moreover, as shown in FIG. 3, the couples Fa and Fb generated at a plurality of positions of the torque ring 5 act so as to rotate the torque ring 5 in the same direction. Therefore, the torque ring 5 directly receives the couple forces Fa and Fb from the hydraulic fluid, and thereby rotates in the arrow X direction. That is, in the illustrated example, when the magnitudes of the couples Fa and Fb are F and the distances between the lines of action are L ₁ , L ₂ and L ₃ , the moment M acting on the torque ring 5 is M = F (L ₁ + L ₂ + L ₃ )
And this moment M causes the torque ring 5 to
Rotates with respect to the pintle 1 and the housing 2. In this case, the volume of the liquid chamber 26 existing in the first area A gradually increases with the rotation of the torque ring 5,
Since the volume of the liquid chamber 26 existing in the region B gradually decreases, the high-pressure fluid successively flows into the liquid chamber 26 passing through the first region A through the first supply / discharge system passage 28, and finishes its work. The fluid is sequentially discharged from the liquid chamber 26 passing through the second region B to the outside of the housing 2 through the second supply / discharge system passage 29. In addition,
From this state, when the pintle 1 is slid to a neutral position where its axis n matches the engine axis m, the forces Fa, F
Since the distances L ₁ , L ₂ and L ₃ between the lines of action of b are zero,
The moment acting on the torque ring 5 is deenergized and the output becomes zero. Further, if the pintle 1 is eccentric in a direction opposite to the illustrated example beyond the neutral position, the couple forces Fa and Fb
Since the distances L ₁ , L ₂ and L ₃ between the lines of action of ₁ become negative, the torque ring 5 is reversed.

Note that FIG. 4 is an explanatory diagram for explaining the principle that torque due to static pressure is directly generated in the torque ring 5.
That is, the couple (Fa, Fb) is moved along its line of action to a position shown in the figure in which the center n of the torque ring 5 is equally spaced, and it is defined as the couple (A, B) (Fa≡ A, Fb≡B). And a virtual couple (C, D) orthogonal to this couple (A, B),
The couples (E, F) that can cancel this couple (C, D) are shown. As is clear from this figure, the force (C + B) and the force (A + D) are equal in magnitude and opposite in direction. That is, (C + B) + (A + D) = 0. Therefore, couple (A, B) + couple (C, D) ≡ 0. On the other hand, as described above, the couple (C, D) + the couple (E, F) ≡ 0. Therefore, the relationship of couple (A, B) ≡ couple (E, F) is established. In other words, the couple (Fa, Fb) is equivalent to the couple (E, F). However, the force E and the force F that form this couple act in opposite directions to each other at positions where the center n of the torque ring 5 is equally spaced, so that only the rotational force acts on the torque ring 5. By directly acting, the force that supports the torque ring 5 becomes unnecessary in principle. That is, when the force f acts on the member S in a manner as schematically shown in FIG. 5a, the member S must be supported by a force corresponding to the force f. Although it cannot rotate, when couples fa and fb act on the member T in a manner as schematically shown in FIG. 5b, the member T rotates without supporting the axis Ta of the member T. You can That is, the axis Ta of the member T is
In order to receive the weight of the member T, it suffices to support it in an auxiliary manner. However, since torque is generated in the torque ring 5 of this embodiment in a manner as shown in FIG. 5b, the force for mechanically supporting the torque ring 5 is very small. Therefore, the deviation of the pintle can be facilitated.

On the other hand, when this hydraulic engine is used as a hydraulic pump, the torque ring 5 is rotationally driven by an external force, for example, in the arrow Y direction. Then, in the case of the illustrated example, the couples Fa and Fb similar to those described above are generated in the torque ring 5,
These couples Fa and Fb are balanced with the input torque applied to the torque ring 2. Then, the liquid outside the housing 2 is sequentially sucked into the liquid chamber 26 passing through the second region B through the second supply / discharge system path 29, and the liquid having a high pressure is passing through the first region A. From the liquid chamber 26 to the first supply / discharge system path 28
It is sequentially discharged to the outside of the housing 2 through.
In this case, when the pintle 1 is slid to the neutral position, the fluid discharge amount becomes zero, and the torque ring 5 idles in a state where the static pressure balance is maintained. Further, when the pintle 1 is eccentric in a direction opposite to the illustrated example beyond the neutral position,
Coupled forces Fa and Fb that are in balance with the input torque are generated in the second region B, and the high-pressure fluid is discharged to the outside of the housing 2 through the second supply / discharge system passage 29.

In the above embodiments, the pintle in which the piston and the cylinder ring are installed is deviated to change the eccentric amount of the cylinder ring with respect to the engine axis. Embodiments in which a fixed amount of displacement with respect to the housing is fixedly supported are included. In this case, it is desirable to fix the pintle 1 to the housing 2 with a fixing screw. As a method of variably performing the deviation, the screw 22 may be manually rotated in addition to the illustrated example. Further, not only the screw type but also the cam type may be used for the displacement. Further, the displacement may be made by a hydraulic servo mechanism. The pintle, torque ring and cylinder ring can also be tapered, in which case the clearance problem can be solved.

〔The invention's effect〕

As described above in detail, according to the present invention, the couple of forces corresponding to the input torque or the output torque is generated in the torque ring only by the static pressure of the fluid introduced into the inner hydrostatic bearing mechanism and the outer hydrostatic bearing mechanism. Since it is obtained, the static pressure of the fluid can be directly converted into the torque of the torque ring. In particular, the piston mechanism is arranged outside the torque ring as compared to the previously proposed rotary fluid energy converter, and the overall size of the engine can be reduced. Further, the sliding range of the piston and the torque ring is small, and the downsizing reduces the range of the peripheral surface of the rotating surface, thus reducing heat generation. Further, the torque ring and the pintle are integrally displaced,
Since there is no synchronization mechanism, the pintle can be smoothly displaced. In addition, the shaft center of the piston mechanism is always oriented toward the center of the engine, so that the piston mechanism can be rotated more smoothly.

[Brief description of drawings]

FIG. 1 is a half sectional view showing an embodiment of the present invention, FIG. 2 is a sectional view taken along the line II--II in FIG. 1, and FIGS. 3 and 4 are explanatory views of the operation of the embodiment. 5A and 5B are views for explaining the operating principle of the embodiment. 1 …… Pintle, 2 …… Housing 3 …… Transmission shaft, 4 …… Inner hydrostatic bearing mechanism 5 …… Torque ring, 6 …… Piston sliding surface 9 …… Cylinder ring, 10,16 …… Gear 11 …… Cylinder hole, 12 …… Piston 12a …… Tip surface, 13 …… External hydrostatic bearing mechanism 21 …… Volume adjustment mechanism, 26 …… Liquid chamber 27 …… Hydraulic passage, 28,29 …… Supply Exhaust system m …… Engine axis center, n …… Pintle axis center Fa, Fb …… Coupling force, d …… Eccentricity

Claims (1)

[Claims] 1. A pintle which is eccentrically arranged with respect to an engine axis and a plurality of inner static pressure bearing mechanisms which are equidistantly arranged in the circumferential direction, are fitted onto the pintle, and the outer periphery of the pintle is fitted. A torque ring having a piston sliding surface formed at a portion corresponding to each inner static pressure bearing mechanism, and an outer periphery of the torque ring concentric with the engine axis and rotatably disposed in the engine housing. And a cylinder ring having a cylinder hole in a portion facing each piston sliding surface, and a piston sliding surface slidably inserted in each cylinder hole of the cylinder ring and each tip of the piston sliding surface on the outer periphery of the torque ring. A plurality of pistons, which are engaged with each other via an external static pressure bearing mechanism, and a hydraulic fluid supply / discharge system that supplies / discharges hydraulic fluid to / from a hydraulic pressure passage formed in a torque ring so as to connect the inner and outer static pressure bearing mechanisms to each other. The road Bei and hydraulic engine, characterized by being configured so as to generate torque in the torque ring by the sum of the couple of the hydraulic static pressure when the hydraulic pressure in the inner and outer side hydrostatic bearing mechanism is introduced.