JP3484604B2 - Spherical rotary piston pump, compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for making a vacuum in a closed container by a power supplied from the outside to suck a fluid and applying a pressure to move it to another place, or as a device for compressing a gas. By incorporating a rotary plate of a rotary piston 3 and a skew plate 5 which rotate in a spherical shape into a housing 1 in a spherical shape, a vacuum portion is formed between the two rotary plates, and the gap volume is changed. The present invention relates to a novel fluid pump and a compressor that perform suction and discharge.

[0002]

2. Description of the Related Art Displacement type pumps in the prior art include circumscribed and inscribed gear pumps, balanced and unbalanced vane pumps, piston pumps roughly classified into axial type, radial type and reciprocating type. is there. Among them, as a hydraulic pump, most of the gear pumps are circumscribing type gear pumps, vane pumps are generally balanced type (constant discharge type) pumps, and piston pumps are of the axial type of axial pumps ( Bent axis type) and swash plate fixed type (swash plate type) are typical.

In the external gear pump, when a pair of external gears meshing with each other rotate in a casing in which the outer periphery and the side face are in close contact with each other, a vacuum portion (space) is formed at a portion where the gears mesh with each other, and a vacuum portion (space) is generated from the suction port. As the working fluid is sucked, this working fluid fills the tooth groove of the suction port, and the working fluid collected in this tooth groove is carried to the discharge port along the inner circumference of the casing by the rotation of the gear, and the gear of the discharge port It is extruded due to the decrease in volume due to the meshing of. This gear pump has a simpler structure, a smaller number of parts, and a lower manufacturing cost than piston pumps and vane pumps, but unlike the other two types of pumps, variable discharge pumps cannot be manufactured.

Although the balanced vane pump is a constant discharge type pump, it can be used at a higher pressure than the non-balanced variable discharge vane pump. This balanced vane pump includes a cam ring fixed in a casing, a bushing pressed and fixed to the side surface of the cam ring, a rotor fixed to a drive shaft (input shaft) surrounded by the cam ring and the bushing, and It is constructed by incorporating vanes. The rotor has a groove cut in the radial direction in which the vane slides freely, because the shaft, the rotor and the cam ring are concentric and the inside curve of the cam ring is almost oval. The vane is always brought into close contact with the inside of the cam ring by the centrifugal force to be driven, and rotates while performing suction and discharge actions. In this balanced vane pump, since the two intake and discharge ports are located symmetrically to each other, the pressure distribution is axisymmetric and the load perpendicular to the axis is not applied.

In the axial type oblique shaft type piston pump, the drive shaft and the rotating cylinder block are mounted in the pump housing at a constant angle (20 to 30 degrees).
In the cylinder block, cylinders are formed parallel to the axis at equal intervals on the circumference, and pistons are inserted into the cylinders. Each of the pistons is connected to the drive shaft flange of the drive shaft through the piston rod and the piston rod end bearing at the end of the piston rod, and reciprocates in the cylinder block to perform suction and discharge operations. The tilt angle is not fixed but is continuously changed from 0 to ± 25 degrees, or 30 degrees, thereby changing the stroke of the piston and making the discharge flow rate variable.

Axial swash plate type (swash,
In the plate type piston pump, the piston reciprocates in the cylinder block similarly to the above-mentioned oblique shaft type piston pump, but unlike the oblique shaft type piston pump, the cylinder block rotates when the shaft is driven, and Each of the pistons arranged inside slides on a tiltable swash plate through a shoe, and reciprocates with a stroke according to the tilt of the swash plate to perform pumping action of suction and discharge. .
This swash plate type piston pump has a smaller number of parts and is smaller than the swash plate type piston pump, and has a simple mechanism and can be made into a variable discharge type by simply changing the inclination of the swash plate.

Since these piston pumps have a longer sliding portion between the cylinder and the piston than gear pumps and vane pumps, they can be used at a high pressure with less leakage of working fluid, and are lightweight, compact and capable of high-speed rotation. Since it is possible, it can be directly connected to a prime mover or a DC motor. Also,
Since the piston pump is a plunger type, theoretically 9
It is a variable discharge type pump that can achieve an efficiency of 0% or more and at the same time has little pulsation of the discharge fluid and can adjust the discharge amount steplessly and reverse the discharge amount. Although it is a long pump, it includes the following drawbacks and problems.

[0008]

[Problems of the prior art] That is, piston pumps in conventional fluid pumps, especially hydraulic pumps, have a more complicated structure than gear pumps and vane pumps, have many parts, require special materials, and require precision machining. The cost is high. Further, since this piston pump repeats the intake / discharge cycle by the reciprocating motion of the piston or the plunger, the motion mechanism and the intake / discharge valve are often worn or broken, and the mechanism or pulsation causes Five to nine pistons are inserted into the cylinder block in order to suppress the fluctuation of the discharge amount, and the effective volume of the stroke volume is small relative to the volume of the entire pump, and the size of the pump body is large. Further, in this piston pump, it is necessary to pay close attention to oil-induced deterioration due to long-term use and dust contamination during disassembly, assembly and operation.

Incidentally, in the vane pump, the vane and the rotor are sandwiched between the cam ring and the bushing and rotate, so that the contact area is large, and high machining accuracy is required for the squareness and dimensions of each part, and the machined surface Roughness is often a problem and the vanes are subject to repeated stresses with each revolution and can be damaged. In addition, since the contact area is large, the viscosity of the hydraulic oil is limited because it is necessary to determine the viscosity of the oil and reduce the gap in order to improve the volumetric efficiency.
If dust is mixed in the used oil or if the oil itself deteriorates, its function will be significantly impaired, so care must be taken when maintaining the oil. That is, the above gear pumps are mostly used at low horsepower at low pressure and low speed rotation except for some parts, piston pumps such as axial type are operated at high pressure and high speed rotation, and vane pumps have intermediate performance between them. is there.

In addition to the compressors, there are reciprocating compressors most widely used in addition to vane compressors, roots blowers, Nash pumps, screw compressors and the like as volume compressors. The compressor body of the reciprocating compressor is divided into a reciprocating part that drives a piston, a container part such as a cylinder and a cylinder head, a suction valve / discharge valve, and a part such as a pipe connected to the crankshaft. Rotation causes the piston to reciprocate through the connecting rod and piston rod, and the reciprocating motion of the piston compresses the air (or gas) that has flowed in from the suction port, and the high pressure and high temperature from the discharge port. It is what is ejected. This reciprocating compressor has a stronger structure and fewer failures than other compressors, and it is relatively easy to handle and maintain and is efficient, but it has a complicated structure and a large number of parts.
The manufacturing cost is high, the vibration is large, the large amount of work is required for the foundation and installation, and there is a risk of explosion and fire due to overheating if maintenance is poor.

[0011]

In view of the many problems that the above-described conventional fluid pump and compressor have, a book composed of a spherical housing and a pair of rotating plates that rotate therein. The fluid pump of the invention has less pulsation of the discharged working fluid (discharging oil), has little change in the discharge amount even if the discharge pressure changes, and has a low pressure from the discharge side inside the pump when the pressure becomes high. There is little leakage to the suction side or inside the case, and it shows high self-priming performance and high overall efficiency (pump efficiency) even in low and high speed regions. In addition, as a compressor, the rotating piston facilitates high-speed and high-pressure operation and exhibits high compression efficiency and mechanical efficiency, so there is no need for multiple stages.
A completely new spherical basic structure fluid pump and compressor that have various performances superior to conventional compressors such as gear pumps, vane pumps, piston pumps, and reciprocating compressors because they are lightweight and compact and have low operating costs. Is provided.

[0012]

In order to solve the above-mentioned problems, the present invention intersects with each other in a hermetically sealed housing 1 having a spherical inner wall surface 7 so as to be coaxially connected so that only a hinge-like movement is possible. Two rotary plates, a rotary piston 3 and a skew plate 5, are incorporated, and the rotary piston 3 is mounted on the input shaft 2 so as to be swingable only in the horizontal direction, and the skew plate 5 is rotated on a fixed axis line. The rotary piston 3
Since the plate surfaces of the swash plate and the skew plate 5 repeatedly approach and separate with rotation, the suction stroke is performed when the plate surfaces are separated from each other to expand and increase the gap, and the plate surfaces approach each other and the gap is increased. Although the discharge process is performed when the amount is reduced and reduced, the present invention generally has the following four solutions.

[0013]

One of the solving means is a housing 1 having an inner wall surface having a spherical surface, and a main bearing 8 is penetratingly provided on a wall of the housing 1 on a straight line passing through a spherical center O of the spherical inner wall 7 to form a straight shaft shape. Of the input shaft 2 is rotatably inserted, and the orbital gap of the circular groove is formed on the inner wall surface of the housing 1 on the vertical plane of the axis intersecting at the spherical center O with an angle θ on the input shaft 2. Cut 9

The input shaft 2 is provided in the housing 1.
And a straight line orthogonal to the ball center O as a connecting axis, swings horizontally on the input shaft 2 within at least an angle (θ × 2),
In addition, the outer peripheral surface is formed as a spherical arc surface 13 that is in sliding contact with the spherical inner wall 7, and the cylindrical intermediate shaft 4 is united on the chord side of which the spherical arc surface 13 is an arc of an arc, and the arc surface 14 is formed on the plate surface. A substantially plate-shaped rotary piston 3 having a central axis O is pivotally connected to the spherical center O of the input shaft 2.

Moreover, in the housing 1, a skewed plate ring 24, which intersects with the rotary piston 3 on the intermediate shaft 4 in a hinge shape and has an outer periphery of an annular shape, is rotatable in the raceway gap 9. And a connecting element for giving a pin and a pin receiving hole to each other on each of both bottom surfaces of the intermediate shaft 4 and both opposite sides of the slanting plate ring 24 facing the both bottom surfaces. A slanting plate 5 of a circular plate which is slidably connected to each other in at least an angle (θ × 2) range and has an arcuate surface 22 on the plate surface.
To provide.

Then, the slanting plate 5 closes the spherical inner wall 7 of the housing 1 to form a semi-lunar working chamber Ha in a hemispherical space.
And the half-moon shaped working chamber Ha of the rotary piston 3
Are formed in the comb-shaped working chamber Fu in the comb-shaped space. Further, the suction hole In and the discharge hole Out are made to face the comb-shaped working chamber Fu.
And a spherical rotary piston pump and a compressor, which are characterized in that and are appropriately provided.

[0017]

As another means for solving the problems, in a housing 1 having an inner wall surface having a spherical surface, a main bearing 8 is provided through a wall of the housing 1 on a straight line passing through a spherical center O of the spherical inner wall 7 to form a straight shaft. The shaft neck of the input shaft 2 in the shape of
Further, a ring-shaped race ring 10 is provided on the circumference of the inner wall surface 7 of the housing 1 on the vertical plane of the axis intersecting at the spherical center O with the input shaft 2 having an angle θ.

The input shaft 2 is provided in the housing 1.
And a straight line orthogonal to the ball center O as a connecting axis, swings horizontally on the input shaft 2 within at least an angle (θ × 2),
Further, a substantially plate-shaped rotary piston 3 having an outer peripheral surface formed on a spherical arc surface 13 in sliding contact with the spherical inner wall 7 and having an arcuate surface 14 on the plate surface.
Is pivotally connected to the spherical center O of the input shaft 2.

Furthermore, in the housing 1, there are provided a raceway bearing 25 of a groove which intersects with the rotary piston 3 in a hinge shape and circulates on the plate surface of the arcuate surface 22 and the outer peripheral surface. A slanting plate 5 of a circular plate is provided on which the orbital ring 10 is fitted in a rotary sliding relationship.

At the intersection of the skew plate 5 and the rotary piston 3, a cylindrical intermediate shaft 4 is divided by a cut surface parallel to both bottom surfaces, and each of them is competed by the skew plate 5 and the rotary piston 3. Each of the divided joint surfaces is provided with a connecting element for providing a pin and a pin receiving hole, and each of them is slidably connected at least within an angle (θ × 2) range.

Then, the slanting plate 5 closes the spherical inner wall 7 of the housing 1 to form a half-moon-shaped working chamber Ha in a hemispherical space, and the half-moon-shaped working chamber Ha is formed by the rotary piston 3 in a comb-shaped space. It is formed in the comb-shaped working chamber Fu. Furthermore, the spherical rotary piston pump and the compressor are characterized in that a suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu.

[0022]

Another solution is to provide a housing 1 having an inner wall surface with a spherical surface, in which a main bearing 8 is provided on a wall of the housing 1 on a straight line passing through a spherical center O of the spherical inner wall 7 to form a straight shaft shape. The shaft neck of the input shaft 2 is rotatably inserted, and the input shaft 2 has an angle θ and is orthogonal to the axis intersecting the ball center O and the axis of the input shaft 2 at the ball center O. Circular holes of the raceway ring bearings 12 are provided on both walls facing the housing 1 on a straight line, and both raceway ring bearings 12 are provided with a raceway ring 6 composed of a ring body rotatably provided in the spherical inner wall 7 of the housing 1. A handle-shaped race ring shaft 11 fixed to the diametrically opposed outer peripheral surfaces is rotatably supported.

In the housing 1, the input shaft 2 is provided.
And a straight line orthogonal to the ball center O as a connecting axis, swings horizontally on the input shaft 2 within at least an angle (θ × 2),
Further, a substantially plate-shaped rotary piston 3 having an outer peripheral surface formed on a spherical arc surface 13 in sliding contact with the spherical inner wall 7 and having an arcuate surface 14 on the plate surface.
Is pivotally connected to the spherical center O of the input shaft 2.

In addition, the housing 1 has a plate surface of the arcuate surface 22 which intersects with the rotary piston 3 in a hinge shape and a track receiver 25 of a groove which circulates on the outer peripheral surface. A slanting plate 5 of a circular plate is provided on which the orbital ring 6 is fitted in a rotary sliding relationship.

At the intersection of the skew plate 5 and the rotary piston 3, a cylindrical intermediate shaft 4 is divided by a cut surface parallel to both bottom surfaces, and each of them is competed by the skew plate 5 and the rotary piston 3. Each of the divided joint surfaces is provided with a connecting element for providing a pin and a pin receiving hole, and each of them is slidably connected at least within an angle (θ × 2) range.

The input shaft 2 is attached to the orbital ring 6.
The inclination angle of the orbital ring 6 from angle 0 to angle ± θ
The control device CA for selecting one of the ranges is set to the orbital ring axis 1
Attach to 1 and work together.

Then, the slanting plate 5 closes the spherical inner wall 7 of the housing 1 to form a half-moon-shaped working chamber Ha in a hemispherical space, and the half-moon-shaped working chamber Ha is formed by the rotary piston 3 in a comb-shaped space. It is formed in the comb-shaped working chamber Fu. Furthermore, the spherical rotary piston pump and the compressor are characterized in that a suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu.

[0028]

As another solution, in a housing 1 having an inner wall surface having a spherical surface, a main bearing 8 is penetratingly provided in a wall of the housing 1 on a straight line passing through a spherical center O of the spherical inner wall 7 to form a straight shaft shape. Of the input shaft 2 is rotatably inserted, and the input shaft 2 has an angle .theta. Are provided on the opposite side of the main bearing 8.

In the housing 1, the input shaft 2 is provided.
And a straight line orthogonal to the ball center O as a connecting axis, swings horizontally on the input shaft 2 within at least an angle (θ × 2),
Further, the rotary piston 3 of a semi-circular plate having an outer peripheral surface formed on a spherical arc surface 13 that is in sliding contact with the spherical inner wall 7 and having an arcuate surface 14 on the plate surface is pivotally connected to the spherical center O of the input shaft 2.

In addition, the housing 1 has an outer peripheral surface which is hinged to the rotary piston 3 and is in sliding contact with the inner wall surface 7 of the housing 1, and an arcuate surface 22 on the plate surface, and the arcuate shape of the arcuate surface 22. A skew plate 5 having a circular plate shape is provided at the center of the back surface side of the surface 22 having a handle-like skew plate shaft 28 into which the skew plate bearing 29 is rotatably inserted.

At the intersection of the slanting plate 5 and the rotary piston 3, a cylindrical intermediate shaft 4 is divided by a cut surface parallel to both bottom surfaces, and each of them is competed by the slanting plate 5 and the rotary piston 3. Each of the divided joint surfaces is provided with a connecting element for providing a pin and a pin receiving hole, and each of them is slidably connected at least within an angle (θ × 2) range.

Then, the slanting plate 5 closes the spherical inner wall 7 of the housing 1 to form a half-moon-shaped working chamber Ha in a hemispherical space, and the half-moon shaped working chamber Ha is formed by the rotary piston 3 in a comb-shaped space. It is formed in the comb-shaped working chamber Fu. Furthermore, the spherical rotary piston pump and the compressor are characterized in that a suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu.

[0033]

[Geometrical Structure] The rotary piston pump and the compressor of the present invention have points, lines, and
There is a characteristic of basic structure that is established on the geometrical figure of the surface. The structure of the invention in its interrelated geometry will be described in detail below.

First, FIG. 1 shows a mutual relationship diagram defining the present invention. A housing 1 formed on an inner wall surface of a spherical surface G having a radius r from a spherical center O has an angle θ. A straight line intersecting at the center O is defined as an X axis line and a Y axis line, and the X
The point where the axis intersects the spherical surface G is P, and the Y axis is the spherical surface G.
Is Q, the point P and the point Q are the diameter of the bottom surface, and the conical generatrix of the conical cone having the apex at the center O of the sphere is U, and the center O is X at the center O. An axis line orthogonal to the axis line is an M axis line, an axis line that intersects both X and Y axis lines at a right angle on the spherical center O is a Z axis line, and both points where the Z axis line intersects a spherical surface G are e and e, and X It is formed by passing through a ball center O in the spherical surface G with the horizontal plane as the axis and the great circular plane in the spherical surface G with the axis L of the diameter segment as the rotation axis, and the Y axis as the vertical axis. The great circle plane is the S circle surface, and the intersection secant at which the R circle surface and the S circle surface intersect at the spherical center O is the axis K, and both ends of the intersection secant K are points K.
a and a point Kb, and the respective relationships of the point, the line, and the surface are set in this way.

When the X-axis and the Y-axis are regarded as fixed-position orientation axes and the X-axis and the Y-axis are rotated at the same time, the S circle surface, which is a vertical plane of the Y-axis, maintains its phase. The R circle surface that rotates as it is and whose axis is the axis of rotation is
It turns while rotating on a conical locus U in the shape of a cone whose base diameter is between the points P and Q of the X and Y axes and the spherical center O is the apex of the cone in the order of FIG. Then, in the rotation of 90 degrees of the rotation, the rotation axis L of the R circular surface revolves a semicircle on the X axis line from FIG. 1 to FIG. 3 and moves on the Y axis line. Further, in the rotation of 90 degrees, the remaining semicircular locus is drawn from the Y-axis through FIG. 4 and returns to the X-axis in FIG. That is, when the rotation axis L of the R circle rotates (revolves) about the circumference of the conical locus U, the R circle rotates about 180 degrees, which is a half rotation, to change the front and back sides.

At that time, the rotation axis L of the R circle surface and the intersecting secant K are always orthogonal to each other at the spherical center O and intersect with the R circle surface and S.
The gap formed between the circle surface and the circle surface is the rotation axis L of the R circle surface.
Is on the X-axis, the vertical angle on the obtuse side becomes 90 + θ angle and becomes the maximum (spaces B and D in FIG. 1 and spaces A and C in FIG. 5), and the vertical angle on the acute angle side becomes 90-θ angle. The minimum (spaces A and C in FIG. 1 and spaces B and D in FIG. 5). That is, the R circle surface and the S circle surface approach each other with a half rotation of each other with the intersection secant K as the axis and the fulcrum of the hinge, and are separated with the next half rotation, and come and go with each rotation. Repeat the separation.

Looking at the spaces A, B, C, and D enclosed by the spherical surface G, the R circular surface, and the S circular surface, the rotation axis L in FIG. In FIG. 5, which makes a half rotation, the space A expands and the space B contracts, and the space C expands and the space D contracts. Further, in the half rotation of the original FIG. 1 through FIGS. 5 to 6, 7 and 8, the space A contracts and the space B expands, the space C contracts and the space D expands. That is, when the space A expands, the space B contracts, and when the space C expands, the space D contracts. Further, the space D contracts as the space A expands, and the space C expands as the space B contracts. Have a relationship. Therefore, the spaces A and B are changed in inverse proportion to each other's volume to form a pair, and the spaces C and D are also changed in inverse proportion to each other's volume to be paired, and the spaces A, C, and B are combined.
And D have an inverse relationship to the order in which the mutual volume changes are directly proportional.

In each of the point, line, and surface relationships set in this way, the spherical inner wall 7 of the housing 1 has the spherical surface G formed by the above-mentioned figure, and the input shaft 2 on the X axis passing through the spherical center O of the spherical surface G is The bearing is supported by being fitted into the main bearing 8 at the point P. Further, on the R circle surface of the geometrical figure, the pin joint joint 16 having the axis M as the base axis of the joint is formed to form the input shaft 2
The skewed plate 5 is placed on the S-circle having the rotary piston 3 connected thereto and having the Y-axis as the axis of rotation. The rotary piston 3 on the R-circle and the oblique plate 5 on the S-circle intersect to form an intermediate shaft 4 on the K-axis, and mutually connect the intersecting secant K to the intermediate shaft 4 of the joint. Hinge joint 1 to be the axis
9 is composed and linked. In addition, the space A in the geometric figure,
B, C, D are two comb-shaped working chambers Fu, Fu, Fu, Fu, Fu formed in the two half-moon shaped working chambers Ha, Ha.
Is.

[0039]

BEST MODE FOR CARRYING OUT THE INVENTION In the present invention, there are embodiments based on the respective configurations of the above solving means 1 to 4, and points, lines, and
The following description will be given based on each surface relationship.

[0040]

First Embodiment One of the forms is the configuration of the solving means 1. That is, in the first embodiment, as shown in FIGS. 9, 10, 15, 18, 19 and 20, the housing 1 having the inner wall surface of the spherical surface G passes through the spherical center O of the spherical inner wall 7. A main bearing 8 of a bearing circular hole is provided at a position P on the wall of the housing 1 through which the X axis passes, and the main bearing 8 rotates a shaft neck of a straight shaft-shaped input shaft 2 having the X axis as a rotation axis. Allow it to be freely inserted and supported. Further, the inner wall of the housing 1 on the extension of the S-circle which is the vertical plane of the Y-axis intersecting at the spherical center O with the angle θ with the input shaft 2 on the X-axis is cut into the orbital gap 9 of the circumferential groove.

Then, on the R circular surface in the housing 1,
The semicircular arcuate surface 14 is formed on the plate surface, and the outer peripheral surface is formed as the spherical arc surface 13 that is slidably engaged with the spherical inner wall 7.
A substantially plate-shaped rotary piston 3 in which a cylindrical intermediate shaft 4 with the axis K attached as an axis is united on the chord side of the arcuate surface 14 having an arc 3 as an arc is arranged and the spherical center O of the input shaft 2 is arranged. The rotary piston 3 and the input shaft 2 are pivotally connected to each other at a position. The rotary piston 3 and the input shaft 2 have a horizontal axis on the input shaft 2 at least at an angle (θ
A pin joint joint 16 composed of a swingable pin and its pin receiver is formed and connected in the range of (2).

Further, on the S-circular surface in the housing 1, the arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 is formed on the plate surface.
A slanting plate 5 having a circular plate and having an annular outer periphery is fitted into the orbital gap 9 and constrained to be rotatable about the Y axis. 3 are arranged so as to intersect with each other in a hinge shape on the intermediate shaft 4, and the intermediate shaft 4
The hinge joint 1 having the K axis as the joint base axis with the two pieces of the pin and the pin receiving hole on the Ka and Kb sides of both bottom surfaces of the slant plate ring 24 facing the both bottom surfaces and the opposing both sides of the slanting plate ring 24.
The rotary piston 3 is connected to the skew plate 5 so as to be slidable in at least an angle (θ × 2) range.

Then, the oblique plate 5 on the S-circle closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form the half-moon-shaped working chamber Ha consisting of a hemispherical constant volume space, and the half moon thereof. The working chamber Ha is formed in the comb-shaped working chamber Fu in the comb-shaped space where the rotary piston 3 on the R circular surface changes in volume. Furthermore,
A suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu of the half-moon shaped working chamber Ha.

[0044]

Second Embodiment Another form is the configuration of the solving means 2. That is, this mode 2 is shown in FIGS.
In the housing 1 having the inner wall surface of the spherical surface G as shown in FIGS. 21 and 21, the main bearing 8 is located at a point P on the wall of the housing 1 through which the X axis passes through the spherical center O of the spherical inner wall 7.
The shaft neck of the input shaft 2 having a straight axis shape with the X axis as the rotation axis is fitted into the main bearing 8 and is supported. Further, the orbit ring of the ring body is formed on the inner wall surface circumference of the housing 1 on the S-circle edge circumference which is the vertical plane of the Y-axis line having the angle θ with the input shaft 2 on the X-axis and intersecting at the spherical center O. 10 is formed in a protruding manner.

Then, on the R circular surface in the housing 1,
The outer peripheral surface is formed into a spherical arc surface 13 that is slidably engaged with the spherical inner wall 7, and a substantially plate-shaped rotary piston 3 whose plate surface is formed into a semi-moon shaped arcuate surface 14 is arranged to form a ball of the input shaft 2. Heart O
Pivot in position. The rotary piston 3 and the input shaft 2 are
The rotary piston 3 has a horizontal axis on the input shaft 2 at least at an angle (θ
The pin joint joint 16 is composed and connected to each other so as to be swingable in the range of (2).

Further, on the S-circular surface in the housing 1, there is an arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 on the plate surface, and the outer circumferential surface is cut into a circular groove on the same circumference. A slanting plate 5 having a circular plate having an orbital support 25 is arranged so as to intersect with the rotary piston 3 in a hinge shape.
The orbital ring 25 is fitted with the orbital groove of the orbital bearing 25 in a sliding contact relationship and is rotatably restrained about the Y axis.

At the intersection of the skew plate 5 on the S circle surface and the rotary piston 3 on the R circle surface, a cylindrical intermediate shaft 4 with the intersection secant K as an attachment axis is parallel to both bottom surfaces. Of the piston intermediate shaft 4a, which is fixed to the rotary piston 3 while being divided into a plurality of cut surfaces, and the slant plate 5.
It is divided into a portion of the slant plate intermediate shaft 4b that is fixedly attached to the slant plate, and the K axis is formed at the joint portion between the piston intermediate shaft 4a and the slant plate intermediate shaft 4b by both pieces of the pin and the pin receiving hole. A hinged joint 19 serving as a joint base line is formed so that the rotary piston 3 is slidably connected to the oblique plate 5 in at least an angle (θ × 2) range.

Then, the oblique plate 5 on the S-circle closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form a half-moon-shaped working chamber Ha consisting of a hemispherical constant volume space, and the half moon thereof. The working chamber Ha is formed in the comb-shaped working chamber Fu in the comb-shaped space where the rotary piston 3 on the R circular surface changes in volume. Furthermore,
A suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu of the half-moon shaped working chamber Ha.

[0049]

[Third Embodiment] Yet another embodiment is a configuration of the solving means 3. That is, in the third embodiment, in the housing 1 having the inner wall surface of the spherical surface G as shown in FIGS. 13, 14 and 17 and 22, the X axis passes through the spherical center O of the spherical inner wall 7. A main bearing 8 is provided at a position P on the wall of the housing 1, and a shaft neck of a straight shaft-shaped input shaft 2 having an X axis as a rotation axis is fitted into the main bearing 8 to be supported.
In addition, a raceway ring bearing 12 having the Z axis as a bearing axis is provided on both walls facing the housing 1 on the points e and e on the Z axis orthogonal to the X axis and the Y axis at the spherical center O. In addition, a ring-shaped race ring shaft 11 having a handle is fixed to each of the opposed outer peripheral surfaces to provide a race ring ring 6 of a ring body rotatable in the inner wall surface 7 of the housing 1. It is fitted in the ring bearing 12 and is rotatably supported.

Then, on the R circular surface in the housing 1,
A sphere of the input shaft 2 is provided by arranging a substantially plate-shaped rotary piston 3 whose outer peripheral surface is formed into a spherical arc surface 13 which is slidably engaged with the spherical inner wall 7 and whose plate surface is formed into a semi-moon shaped arcuate surface 14. The rotary piston 3 and the input shaft 2 are pivotally connected to the center O position.
The rotary piston 3 has a horizontal axis on the input shaft 2 at least at an angle (θ ×
The pin joint joint 16 is composed and connected with both pieces so as to be swingable in the range of 2).

Further, on the S-circular surface in the housing 1, there is an arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 on the plate surface, and the outer circumferential surface is cut into a circular groove on the same circumference. The slanting plate 5 having a circular plate having the formed orbit receiver 25 is arranged so as to intersect with the rotary piston 3 in a hinge shape.
Is fitted to the orbital ring 6 in a circular groove of the orbital bearing 25 in a sliding contact relationship and is rotatably restrained about the Y axis.

At the intersection of the skew plate 5 on the S-circle and the rotary piston 3 on the R-circle, a cylindrical intermediate shaft 4 with the intersection secant K as an attachment axis is parallel to both bottom surfaces. The cut face is divided into a plurality of parts, and is divided into a piston intermediate shaft 4a portion fixed to the rotary piston 3 and a slant plate intermediate shaft 4b portion fixed to the slant plate 5, and the piston At the joint portion between the intermediate shaft 4a and the skew plate intermediate shaft 4b, a hinge joint 19 having a K axis as a joint base axis is formed by both pieces of a pin and a pin receiving hole, and a rotary piston 3 is provided on the skew plate 5. Connects at least in the range of angle (θ × 2) so as to be slidable.

Incidentally, the orbital ring 6 has a phase control device CA for orbital 6 phase for freely changing the tilt angle of the orbital ring 6.
Is attached to the orbital ring shaft 11 and is interlocked, and the tilting of the orbital ring 6 about the orbital ring shaft 11 on the Z-axis is made from the angle 0 to the angle ± θ with respect to the X-axis line of the input shaft 2. Let the controller CA automatically select any of the ranges.

Then, the slanting plate 5 on the S-circle closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form a half-moon-shaped working chamber Ha consisting of a hemispherical constant volume space, and the half moon thereof. The working chamber Ha is formed in the comb-shaped working chamber Fu in the comb-shaped space where the rotary piston 3 on the R circular surface changes in volume. Furthermore,
A suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu of the half-moon shaped working chamber Ha.

[0055]

[Fourth Embodiment] Still another embodiment is a configuration of the solving means 4. That is, in this mode 4, in the housing 1 having the inner wall surface of the spherical surface G as shown in FIGS. 23 and 24, the X axis passes through the spherical center O of the inner spherical surface wall 7 of the housing 1 toward the point P side. The main bearing 8 is provided so that the shaft neck of a straight shaft-shaped input shaft 2 having the X axis as the axis of rotation is fitted into the main bearing 8 so as to be supported, and the angle of the input shaft 2 on the X axis is θ. A circular hole for the skewed plate bearing 29 is also provided on the opposite side of the main bearing 8 in the housing 1 wall on the Y-axis line that intersects at the spherical center O.

Then, on the R circular surface in the housing 1,
A rotary piston 3 of a semicircular plate having an outer peripheral surface formed on a spherical arc surface 13 slidingly engaged with the spherical inner wall 7 and a plate surface formed on a semi-lunar arcuate surface 14 is arranged to dispose the rotary shaft 3 of the input shaft 2. Pivot at the ball center O position. The rotary piston 3 and the input shaft 2 have X
The rotary piston 3 has a horizontal axis on the input shaft 2 at least at an angle (θ ×
The pin joint joint 16 is composed and connected with both pieces so as to be swingable in the range of 2).

Further, on the S-circular surface in the housing 1, an outer peripheral surface which is in sliding contact with the inner wall surface 7 of the housing 1 forming a spherical surface G and an arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 are provided on the plate surface. In addition, a skewed plate 5 of a circular plate having a circular rod-shaped skewed plate shaft 28 fixed to the central portion on the back surface side of the arcuate surface 22 is arranged so as to intersect the rotary piston 3 in a hinge shape. The skew plate 5 is rotatably supported by inserting the skew plate shaft 28 having the Y axis as a rotation axis into the skew plate bearing 29.

At the intersection of the skew plate 5 on the S-circle and the rotary piston 3 on the R-circle, a cylindrical intermediate shaft 4 having the intersection secant K as an attachment axis is parallel to both bottom surfaces. Of the piston intermediate shaft 4a, which is fixed to the rotary piston 3 while being divided into a plurality of cut surfaces, and the slant plate 5.
It is divided into a portion of the slant plate intermediate shaft 4b that is fixedly attached to the slant plate, and the K axis is formed at the joint portion between the piston intermediate shaft 4a and the slant plate intermediate shaft 4b by both pieces of the pin and the pin receiving hole. A hinged joint 19 serving as a joint base line is formed so that the rotary piston 3 is slidably connected to the oblique plate 5 in at least an angle (θ × 2) range.

Then, the oblique plate 5 on the S-circle closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form the half-moon-shaped working chamber Ha consisting of a hemispherical constant volume space, and the half moon thereof. The working chamber Ha is formed in the comb-shaped working chamber Fu in the comb-shaped space where the rotary piston 3 on the R circular surface changes in volume. Furthermore,
A suction hole In and a discharge hole Out are appropriately provided so as to face the comb-shaped working chamber Fu of the half-moon shaped working chamber Ha.

[0060]

[Common mode of each embodiment (formation of working chamber and θ angle)]
In the present invention, the number of working chambers formed in the housing 1 is the following three as a common aspect in the first to third embodiments and the first to fourth embodiments. Common mode 1
(4 working chambers). In the first to third embodiments described above, the half-moon shaped working chambers Ha and Ha are formed on both sides of the oblique plate 5, and each of the two half-moon shaped working chambers Ha and Ha is provided with two circular plate-shaped rotary pistons 3. Each comb-shaped working chamber Fu, Fu, Fu,
It is formed in Fu (spaces A, B, C, D). Common mode 2
(2 working chambers arranged horizontally to the axis of rotation). In the above-described first to third embodiments, the half-moon-shaped working chambers Ha, Ha are formed on both sides of the slanting plate 5, and the two half-moon-shaped working chambers Ha, Ha,
A rotating piston 3 having a hemispherical plate forms each of Ha in the comb-shaped working chambers Fu and Fu (spaces A and D or spaces B and C). Common mode 3 (two working chambers arranged in a direction perpendicular to the rotation axis). In the first to fourth embodiments described above, the half-moon-shaped working chamber Ha is formed only on one of the two sides of the oblique plate 5, and the half-moon-shaped working chamber Ha has a semi-circular plate-shaped rotary piston 3 in two comb shapes. Working chamber Fu, Fu (space A, B or space C,
D).

In any of the above embodiments,
The tilt angle θ created by the X axis line and the Y axis line intersecting at the spherical center O has a practical range of 10 ° <θ <60 °, and the optimum angle is 25 ° to 35 °.

[0062]

[Principle of Operation] The principle of operation of the spherical rotary piston pump and compressor of the present invention having the above-described structure is illustrated in the rotation interlocking of the rotary piston 3 and the skew plate 5 and the accompanying volume change of each working chamber Fu. 25 and 26, the first embodiment and the common mode 1 will be taken as an example, and the mounting of the working fluid inlet / outlet holes In and Out and the entire operation of the suction and discharge strokes will be described below with reference to FIG.

When the input shaft 2, the rotary piston 3, and the skew plate 5 in FIG. 25 (a) are in the engaged state with the pin joint joint 16 and the hinge joint 19 interposed, the input shaft 2 When the motor is rotated by an electric motor or a prime mover such as an internal combustion engine, the rotary piston 3 is guided on the plane of rotation of the skew plate 5 to rotate the ball center O of the inner wall surface 7 of the housing 1 which is the common center of the three. A conical motion is performed along the conical locus U as the center. That is, FIGS. 25 and 26 (a) to (l) show a half rotation (180 degrees) between the rotary piston 3 and the skew plate 5 which rotate in cooperation.
Degree) minutes.

Further, the comb-shaped working chamber Fu shown in the drawing is
First, the inside of the sphere of the housing 1 is formed into two half-moon shaped spaces Ha, Ha in which the concave inner wall surface 7 is closed by the slanting plate 5, and further the rotary piston 3 incorporated therein forms an oblique relation with the inner wall surface 7 of the housing 1. Comb-shaped spaces A, B, C, and D surrounded by the arcuate surface 22 of the row plate 5 and the arcuate surface 14 of the rotary piston 3 including the intermediate shaft 4 pillar surface, but the same half-moon-shaped working chamber The comb-shaped working chambers A and B or C and D formed in Ha operate by changing the working chamber volume in inverse proportion to each other.

That is, if the rotary piston 3 configured as a double end piston is incorporated into each of the half-moon shaped working chambers Ha, Ha formed at the double end by the slanting plate 5 and operated, the same half-moon shaped working chamber is formed. When the space on one of the two comb-shaped working chambers A and B or C and D in Ha expands to increase the volume, the space on the opposite side contracts to decrease the volume, and the slant plate The two working chambers A and D or the spaces B and C sandwiching the same arcuate surface 22 of 5 also operate by changing their volumes in inverse proportion to each other. The two working chambers A and C, and the two working chambers B and D, which are opposed to each other with the oblique plate 5 sandwiched therebetween, change in an increasing / decreasing relationship in which their volumes are always directly proportional.

After all, the formation of the comb-shaped space is a gap between the plate surfaces of the rotary piston 3 and the skewed plate 5 which face each other, and the space volume thereof increases or decreases depending on the mutual separation of the plate surfaces. Therefore, if the plate surface gap is defined as the working chamber Fu space, the mutual approach of the plate surfaces of the rotary piston 3 and the skewed plate 5, which are given to each other, is the contraction of the gap formed between the plate surfaces and the operation is performed. Volume reduction in the chamber Fu space, which corresponds to the operation of the reciprocating piston pump, the piston in the reciprocating compressor, or the plunger in the cylinder from the bottom dead center to the top dead center of two dead points. . On the contrary, the spacing between the plate surfaces of the rotary piston 3 and the oblique plate 5, which are given to each other, is an increase in the space volume, and the reciprocating piston pump, the piston in the reciprocating compressor, or the plunger is bottom dead from the top dead center. This corresponds to the process of moving to a point, and the relaxation and contraction of the gap formed between the plate surfaces are the increase and decrease of the volume in each working chamber Fu.

In FIG. 25 (a), the working chamber A has its working chamber gap contracted to the minimum volume, and the working chamber C at the symmetrical position of the working chamber A also contracts the working chamber gap. The working chamber B shares the same half-moon shaped working chamber Ha with the working chamber A, and the working chamber D sharing the other half-moon shaped working chamber Ha with the working chamber C has a working chamber gap. Has an upper limit volume that is expanded. The rotary piston 3 in FIG. 25 (a) is placed on the input shaft 2 in symmetrical equilibrium, the intermediate shaft 4 is orthogonal to the input shaft 2, and the axis of the input shaft 2 and the center line of the piston through hole 15 are aligned. And are in a state of overlapping.

In this case, the rotary piston 3 swings in the plane direction on the input shaft 2 with the input shaft 2 as the amplitude baseline, but when the input shaft 2 is rotated in the direction of the arrow, the piston through-hole 1
Horizontal balance line (axis L) of the rotating piston 3 passing through the center of 5
Is gradually deviated from the input shaft 2 and biased, and the working chambers A and C are expanded in volume in order of FIG. 25 (a) to (b), (c), (d), and (e) to expand the volume. On the contrary, in the working chambers B and D, the plate surfaces of the rotary piston 3 and the slanting plate 5 approach each other to shrink the working chamber space and reduce the volume thereof.

Then, as shown in FIG. 26 (g), the rotary piston 3 moves by an opening angle (tilt angle θ) created between the axes of the input shaft 2 and the skew plate 5, which is the input shaft 2. Corresponding to a rotation angle of 90 degrees, the four working chamber spaces A, B, C,
The volume change of D becomes medium and each volume becomes equal, but if the operation further proceeds in the direction of FIGS. 26 (h) to (k), the gap between the working chambers of the working chambers A and C is increased. Further expands and increases the volume, and conversely further decreases the volumes of the working chambers B and D. That is, the rotary piston 3 in FIG.
Is a half rotation of 180 degrees, the front and back of the rotary piston 3 are exchanged as shown in FIG. 26 (l), the working chambers A and C both expand the working chamber gap, and the volume becomes the maximum amount. On the contrary, the working chambers B and D shrink their volumes from the upper limit value to the lower limit value.

The volume change of each working chamber A, B, C, D from FIG. 25 (a) to FIG. 26 (l) is the amount of rotation of 180 degrees, but the working chamber A in FIG. 25 and C until the gaps between them are both lower limits and the gaps between the working chambers B and D are both upper limits, as shown in FIG.
From (a), it means that one rotation, which is 360 degrees, is performed, and each of the working chambers A, B, C, and D has rotated enough to complete two strokes of suction and discharge. become. Therefore, if the suction hole In and the discharge hole Out are provided at appropriate positions in the housing 1 to supply the working fluid, and the two-stroke cycle as described above is repeated, the spherical rotary piston pump and the compressor of the present invention can be obtained. Operates as a fluid pump and compressor. At that time, especially as a compressor, the discharge hole Out
A valve such as a check valve (check valve) may be installed on the side.

[0071]

[Stroke] In the spherical rotary piston pump and compressor of the present invention, the volume change of the comb-shaped working chamber Fu alternating from the minimum to the maximum and from the maximum to the minimum is, as described above, one of the two rotation angles of the input shaft.
It is performed every 80 degrees and has two strokes of suction stroke and discharge (compression) stroke like the conventional reciprocating piston pump, compressor or vane pump of constant discharge capacity, and the full operation of the two strokes. Is performed during 360 degrees of shaft rotation, that is, during one rotation of the input shaft 2. Further, in the spherical rotary piston pump and compressor of the present invention, regardless of whether the working fluid is a liquid or a gas, the flow path hole through which the fluid flows in and out is the suction hole In and the discharge hole In to each crescent-shaped working chamber Ha. At least one hole Out is formed at a position substantially opposite to the wall of the housing 1, and the entrance and exit holes In and Out in that case are on a plane passing through both the X and Z axes shown in the geometrical configuration. It opens to the inner wall surface 7 of the housing 1.

FIG. 27 shows the operating process of the spherical rotary piston pump and compressor of the present invention. The intake and discharge strokes will be described below. [Suction stroke (-)] In the state of Fig. 27 (A), the volume of the working chamber Fu is minimum, and corresponding to the top dead center of the suction side, (B)-(D) and the rotary piston 3 are shown. The working chamber Fu is gradually increased with the rotation of the
Working fluid is drawn from the. Then, in the state of (A), the volume of the working chamber Fu becomes maximum and the suction stroke ends, but this state corresponds to the bottom dead center position on the suction side. [Discharge Stroke (-)] At the end of the suction stroke (A), the discharge hole Out opens near the bottom dead center to start compressing the sucked fluid, and at the same time, the fluid begins to be discharged as a liquid and is not gas. The discharge timing is adjusted by a discharge valve, a check valve, etc. attached to the discharge hole Out, and (B) to (D)
After that, the discharge is continued up to the vicinity of (A).

As described above, in the spherical rotary piston pump and compressor of the present invention, the two comb-shaped working chambers Fu and Fu in each half-moon shaped working chamber Ha are provided during one rotation of the rotary piston 3.
Since each of them completes the suction stroke and the discharge stroke, there is a feature that the rotary piston 3 and the input shaft 2 have one discharge stroke per one rotation. The displacement volume of the spherical rotary piston pump and compressor of the present invention is proportional to the volume of the entire working chamber Fu.

[0074]

[Performance Calculation] The performance calculation of the spherical rotary piston pump and compressor of the present invention will be described in terms of a fluid pump.
Its performance is similar to that of conventional pumps.
n], and the discharge amount Q is expressed by the following equation. Q = (ηυ · qp · N) / 1000 ηυ Volumetric efficiency of the pump qp Displacement volume per revolution of the pump [cm ³ / re
v] N input rotation speed [rpm] At this time, the input Ln [kW] necessary for causing the spherical rotary piston pump of the present invention to work is also calculated by the following equation, as in the conventional pump. Ln = (P ・ Q) / (60 ・ η) P Discharge pressure [MP
a] (= 100 / 9.8 [kgf / cm ² ]) η Total efficiency (pump efficiency) Q Discharge rate [l / min] The total efficiency η is the volumetric efficiency ηυ multiplied by the mechanical efficiency ηm.

[0075]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As described above, the spherical rotary piston pump and compressor according to the present invention are characterized in that each of the common modes 1 to 3 in the various embodiments (1 to 4) is based on the above operating principle, and It operates as a compressor. That is, in the present invention, one comb-shaped working chamber to four comb-shaped working chambers (Fu or Fu, F) are provided in the housing 1.
u or Fu, Fu, Fu or Fu, Fu, F
u, Fu), but particularly in the above-mentioned Embodiments 1 to 3, four comb-shaped working chambers Fu, Fu, Fu, Fu (spaces A, B, C, D), or the above-mentioned modes 1 to 3
In one housing 1, two comb-shaped working chambers Fu and Fu (spaces A and D) arranged in the horizontal direction with respect to the rotation axis are provided.
Or the spaces B, C) are formed, or, in the above-mentioned Embodiments 1 to 4, two comb-shaped working chambers Fu, Fu (spaces A,
Three types of forms forming B or spaces C and D) will be described in detail with reference to the drawings based on the following embodiments.

[0076]

[First Embodiment] First, an embodiment in which four comb-shaped working chambers A, B, C and D are formed in one housing 1 will be described. This example shown in FIGS. 9 and 10 is an example based on the configurations of the first embodiment and the common mode 1. For example, assuming that the housing 1 in which the relations of points, lines, and planes are set in the above-mentioned solving means are separated by two parallel cut face planes that straddle the S circle surface of aa and bb shown in FIG. 1 is divided into 3 parts, and is divided into a central part on the S circle surface which is cylindrical or annular and both side parts each consisting of a spherical crown smaller than a hemisphere, and the oblique plate 5 can be rotated at the central part. Is formed on the inner wall surface of the S-circular surface concentric with the sloping plate housing 1b that is larger than the spherical surface G, and the both sides of each of the rotary piston housings 1a and 1a that enclose the semicircle of the circular rotary piston 3 are from the spherical surface G. Are formed on the inner walls 7a, 7a of the symmetrical concave surface.

When the inclined plate housing 1b and the rotary piston housings 1a, 1a on both sides are united to form a spherical integral structure, both rotary piston housings 1a whose inner surface is the groove bottom are formed. , 1a are formed between the circumferential edges of the concave inner walls 7a, 7a as the orbital gaps 9 which are groove-shaped gaps which circulate along the extension plane of the S-circle. Then, the rotary piston housing 1a on the X axis which intersects the Y axis of the center line of the orbital space 9 at the spherical center O at an angle θ.
Main bearings 8 and 8 having bearing holes are formed through both opposite walls of 1a, and both side shaft necks of an input shaft 2 having a straight axis shape with the X axis as a rotation axis are inserted into both main bearings 8 and 8. And allow it to rotate freely. The input shaft 2 is provided with a connecting element formed of either a pin column of the pin joint joint 16 or a pin receiving hole located at the center O of the ball and having the M axis as a connecting shaft (see FIGS. 9 and 10).
Which is a pin receiving hole).

Further, on the R circular surface inside the housing 1, the concave inner wall 7 of each rotary piston housing 1a forming a spherical surface G is formed.
a spherical arc surface 13 on the outer peripheral surface rotatably slidingly contacting a, and front and back arcuate surfaces 14 and 14 forming an arcuate contour plane of the spherical arc surface 13.
And two of the bow-shaped plates formed by the bow-shaped surfaces 14 and 14 on the front and back sides and the chord side surfaces sandwiched by the bow-shaped chords are symmetrically arranged with their chord-side surfaces facing each other with the K axis interposed therebetween. A rotary piston 3 having a generally circular plate as a whole is arranged by interposing a cylindrical intermediate shaft 4 having the K axis as an attachment axis on the chord side surfaces of both arcuate plates.

A piston which penetrates the rotary piston 3 from both spherical arc surfaces 13, 13 on the X-axis toward the center of the intermediate shaft 4 along the R-circle contained therein to allow the input shaft 2 to be loosely inserted. The pin joint joint 1 is formed so that the through hole 15 is opened and at the center of the piston through hole 15 inside the intermediate shaft 4 the M axis is used as the connecting axis and corresponds to the shaft center 17 of the input shaft 2.
A piston pivot 18 of 6 (which is a pin post in FIGS. 9 and 10) is provided. Then, the piston pivot 18 is pivotally attached to the axial center 17 of the input shaft 2 so as to be rotatable within an angle range of ± θ with respect to the input shaft 2 on the X axis. In addition, the intermediate shaft 4 of the rotary piston 3
At either end, either the hinge pin 20, 20 of the hinge joint 19 or the hinge pin receiver 21, 21 (the hinge pin receiver in FIGS. 9 and 10 is used on the side of the point Ka and the point Kb as the connecting axis). 21 and 21).

The opening of the piston through-hole 15 having an elliptical shape has a minor axis slightly larger than the axial diameter of the input shaft 2, and a major axis of the rotational axes X and Y of the input shaft 2 and the skew plate 5. Crossing angle θ
The rotation piston 3 apparently reciprocally oscillates on the input shaft 2 as the rotation piston 3 rotates. Therefore, the rotary piston 3 rotates with the input shaft 2 while swinging only in the major axis direction of the piston through hole 15 with respect to the input shaft 2, and reciprocates once in the major axis direction of the piston through hole 15 per one rotation of itself. .

On the other hand, on the S-circular surface in the housing 1, symmetrically-shaped arcuate surfaces 22, which respectively correspond to the arcuate surfaces 14, 14 of the rotary piston 3, on opposite sides of the rotary piston 3 with the intermediate shaft 4 interposed therebetween. Two of the bow-shaped plates formed by having the front and back sides of 22 and the chord side surface of the intermediate shaft 4 on the chord side of the bow-shaped surfaces 22 and 22 and the chord side surface 23 on which the geometric condition is slidably contactable, An annular slant plate ring 24 fitted in the raceway gap 9 so as to be rotatable and slidable.
Slanting plate 5 formed into one circular plate by being connected to the inside of
Are placed. That is, the oblique plate 5 is formed by a bow-shaped inferior arc smaller than a semicircle and an arcuate chord that passes both ends of the inferior arc on the same plane, and the arcuate contour surfaces of the arcuate plates that are symmetrically arranged are located outside. Facing each other chord side surfaces 23, 23, and arranging a slanting plate ring 24 formed on the inner peripheral surface that engages with both arcuate contour surfaces on the outer side of each arcuate plate to connect them. For example, the whole shape is formed into a circular plate.

In addition, the oblique plate 5 has four sides facing the chord side surfaces 23, 23 facing each other across the K axis and the opposite surfaces of the oblique plate ring 24 facing on the K axis. A window-shaped void portion is formed which penetrates the K-axis in a rectangular shape, and the skewed plate ring 2 is located at points Ka and Kb of the void portion.
On both opposite sides of 4, a connecting element (indicated by hinge pins 20, 20 in FIGS. 9 and 10) corresponding to the hinge joint 19 element attached to both ends of the intermediate shaft 4 of the rotary piston 3 is provided. Then, if the intermediate shaft 4 of the rotary piston 3 is fitted into the window-like space of the skew plate 5 along the axial column, both opposite sides of the skew plate ring 24 in the window frame and both ends of the intermediate shaft 4 are attached. The hinge pins and the hinge pin receivers 20, 21, 20, 21 are fitted together, and the chord side surfaces 23, 23 of the slanting plate 5 and the shaft column surface of the intermediate shaft 4 are sealed in a sliding contact relationship, so that the intermediate shaft 4 Both bottom surfaces and the opposing surfaces of the skew plate ring 24 that remains as a window frame are also sealed in a sliding contact relationship, and two circular plates of the rotary piston 3 and the skew plate 5 are the intermediate shafts 4.
It is assembled so that it can be slidably crossed within the ± θ angle range with the intersection secant K as the axis of connection.

In the end, the semicircles of the rotary pistons 3 thus assembled to the oblique plate 5 are provided by the semicircular circles, and the concave inner walls 7a of the rotary piston housings 1a, 1a are provided.
The spherical arcuate surfaces 13, 13 are accommodated in 7a while being held in a non-immediately separated state, and the oblique plate ring 24 of the oblique plate 5 is rotatably fitted in the raceway space 9 of the oblique plate housing 1b. The input shaft 2 and the rotary piston 3 form a pin joint joint 16 in the inner center of the rotary piston 3 and are connected to each other, and the rotary piston 3 and the skew plate 5 are hinged at both ends of the intermediate shaft 4. The joint 19 is composed and connected.

Then, the oblique plate 5 on the S-circle closes the concave inner walls 7a, 7a of the rotary piston housings 1a, 1a to form a hemispherical half-moon shaped working chamber H in a constant volume space on both sides thereof.
a, Ha, and each of the half-moon shaped working chambers Ha, Ha has two comb-shaped working chambers A, B and C, in which the rotary piston 3 on the R-circle changes volume inversely proportionally. Form D. Further, there are provided a suction hole In and a discharge hole Out for the working fluid, which penetrate the wall of the housing 1 so as to face the respective half-moon shaped working chambers Ha.

Then, when the input shaft 2 is rotated in the direction of the arrow, the rotation of the input shaft 2 is transmitted to the pin joint joint 16 and, as shown in FIGS. Rotating the rotating piston 3 and the skew plate 5 in cooperation with each other,
Along with this, the plate surface gap between the rotary piston 3 and the oblique plate 5 changes, and the volume of each of the working chambers A, B, C, D formed between the plate surfaces also increases or decreases. When the volumes of the working chambers A, B, C, and D increase, the working fluid is sucked through the suction holes In provided by each of the working chambers, and when the volumes of the working chambers A, B, C, D decrease, the working fluid is discharged from the discharge holes Out provided by the respective working chambers.

[0086]

[Embodiment 2] This embodiment shown in FIGS. 11 and 12 is based on the construction of the second embodiment and the common mode 1, and four comb-shaped actuations are provided in the housing 1 in the same manner as the construction of the first embodiment. The chambers A, B, C and D are formed, but in order to restrain the phase of the skew plate 5, the skew plate ring 24 and the skew plate ring 24 are formed.
In contrast to the first embodiment, which is configured with the orbital gap 9 of the orbital groove to which is fitted, in this embodiment, the oblique plate ring 24 is not attached to the oblique plate 5, and instead the oblique plate is attached. 5 has a raceway bearing 25 of a groove that circulates the outer peripheral surface of 5, and a raceway ring 10 of a ring body fitted to the raceway bearing 25 is fixed to the inner wall surface 7 of the housing 1 on the S circle surface. On the inner wall surface 7, a convex ring is attached to the concave groove of the raceway gap 9 in the first embodiment.

Further, in the main bearings 8 and 8 at the points P and P, the input shaft 2 having the shaft center 17 of the pin joint joint 16 in the portion of the ball center O is the same as in the first embodiment. The rotary piston 3 on the R circular surface on which the input shaft 2 is inserted and pivotally supported is a circular plate in which the intermediate shaft 4 is interposed between two arcuate plates symmetrically arranged. Also, the skew plate 5 placed on the S circle surface on the orbit ring 10 is also a circular plate in which the intermediate shaft 4 is interposed between two symmetrically arranged arcuate plates.

Incidentally, the four pillars of the intermediate shaft in the second embodiment are
The shaft cylinder is cut into parallel pieces on both bottom parallel planes into a plurality of pieces (3 divisions in FIGS. 11 and 12), and the central portion thereof is fixed to the arcuate chord side of the rotary piston 3 as the piston intermediate shaft 4a. Both end portions are fixed to the arcuate chord side of the skew plate 5 as the skew plate intermediate shafts 4b, 4b, and the piston intermediate shaft 4a and the skew plate intermediate shafts 4b, 4 of the wheel-slicing joint portion are fixed.
A hinge pin and a hinge pin receiver 20, 21, 20, 21 which give each other a K axis as a base axis of the connection at the center of the bottom surface with b.
And are connected to each other to form the hinge joint 19. Also,
As described above, the skew plate 5 includes the skew plate intermediate shafts 4b, 4b.
The raceway receiver 25 of the groove that surrounds the outer peripheral surface including the bottom surface on the rotary centrifugal side is cut so that the raceway ring 10 is rotatably fitted.

After all, also in this embodiment, the inner wall surface 7 of the housing 1 forming the spherical surface G is formed on the concave inner walls 7a, 7a which face each other with the orbital ring 10 of the internal projection provided as a boundary, and the concave inner walls 7a, 7a are inclined. By incorporating the row plate 5, it is formed in the constant volume space of the two half-moon shaped operation chambers Ha, Ha, and the semicircular operation of the semicircular portions of the rotary pistons 3 are accommodated in the concave inner walls 7a, 7a in an improper manner. Each of the chambers Ha, Ha is formed into two sealed comb-shaped working chambers A, B, C, D that change volume inversely. Then, when the input shaft 2 is rotated in the direction of the arrow, the rotation of the input shaft 2 causes the rotary piston 3 and the skew plate 5 to rotate in cooperation with each other as in the case of the first embodiment, so that the respective working chambers A, B and C are rotated. , D, the volume is changed, and when the volume is increased, the working fluid is sucked from the suction hole In formed at an appropriate position on the wall of the housing 1, and the discharge hole is similarly formed when the volume is decreased. Exhaust working fluid from Out.

[0090]

[Third Embodiment] The orbital ring 10 fixedly attached to the inner wall surface 7 of the housing 1 in the second embodiment can be configured as a movable portion in the housing 1. That is, FIG. 13 and FIG. 1 based on the configuration of the third embodiment and the common mode 1
In this embodiment shown in FIG. 4, the fixed raceway ring 10 in the second embodiment is replaced with the movable raceway ring 6, and the control device CA is newly attached to the raceway ring 6, but The controller CA sets the tilt angle of the skew plate 5 to 0.
The discharge flow rate is made variable by changing the stroke of the rotary piston 3 by continuously changing the angle to ± θ.

In other words, in this embodiment, the handle ring ring is composed of the outer peripheral surface which can be rotated in the direction of the ring axis within the inner wall surface 7 of the housing 1 and the round columns which are fixed to both outer peripheral surfaces facing each other on the diameter center line. An orbital ring 6 formed of a ring body having axes 11 and 11 and movable only in the right and left directions on both X and Y axes is provided, and an opposing wall of the housing 1 on the Z axis corresponding to the points e and e. Orbit ring bearings 12, 12 with the Z axis as the bearing axis
To provide. Then, the orbital ring 6 is rotatably fitted to and mounted on the orbital bearing 25 of the orbiting groove of the oblique plate 5, and the orbital ring shafts 11 and 11 are rotatably fitted to the orbital ring bearings 12 and 12. Although not shown in the figure, a control device CA for inserting and supporting it, further attaching a connecting terminal to the shaft neck of the orbital ring shaft 11, 11 and freely changing the tilt angle of the skew plate 5 at the terminal of the shaft neck. Connect the terminals of.

Then, the controller CA displaces the fixing stop positions of the orbital ring shafts 11 and 11 according to the pump discharge pressure, and the displacement of the fixed position passes through the orbital ring 6 and the tilt angle of the skew plate 5 ( 0 to ± θ) is automatically changed, but the change in the inclination of the skew plate 5 changes the swing stroke of the rotary piston 3, and the stroke becomes longer when the inclination becomes large and becomes shorter when the inclination becomes smaller. The absolute volume amount, which is the displacement volume of each comb-shaped working chamber A, B, C, D in one rotation of the shaft, is changed to secure a necessary discharge amount according to the discharge pressure.

[0093]

[Fourth Embodiment] In the constructions of the first to third embodiments, four working chambers Fu, Fu, Fu, Fu, Fu are provided in the housing 1.
From the configuration, it is possible to operate in a two working chamber Fu, Fu configuration. This embodiment shown in FIG. 15 is based on the first embodiment and the common mode 2, and in the configuration of the first embodiment, the four working chambers A, B, C and D are axially arranged into two working chambers A and D. Alternatively, the two working chambers B and C are used instead.

Incidentally, this embodiment is similar to the above-mentioned embodiment 1,
The housing 1 in which the respective relationships of points, lines, and planes are set in the solution means is divided into three parts by two parallel planes of cuts a-a and a-b shown in FIG. As the slanting plate housing 1b, each of both side portions is the rotating piston housings 1a and 1a, and when they are combined on the same line, the inside of the slanting plate housing 1b rotatably restrains the slanting plate ring 24. The input shaft 2 is formed in a groove-shaped gap as 9 and has a shaft center 17 of the pin joint joint 16 element at the position of the ball center O on the opposing walls of the rotary piston housings 1a on the X axis. The main bearings 8, 8 which are inserted and supported are penetrated.

On the other hand, in contrast to the first embodiment, in the present embodiment, the circular rotary piston 3 has a spherical arc surface 13 on the outer peripheral surface of rotation and both chord sides on the same plane sandwiching the K axis. The substantially circular plate rotary piston 3 having a hemispherical shape as a whole is composed of the arcuate surfaces 14 and 14 and the cylindrical intermediate shaft 4 that is semi-embedded between the arcuate surfaces 14 and 14, and the above-mentioned embodiment is used. 1, the rotary piston 3 has a piston shaft hole 15 into which the input shaft 2 is loosely inserted, and a piston pivot 18 of the pin joint joint 16 located at the ball center O and hinge joints at both ends of the intermediate shaft 4. And 19 connecting elements.

Further, in contrast to the first embodiment, in contrast to the circular skew plate 5 formed by connecting the skew plate ring 24 to the two symmetrically arranged arcuate plates, the skew in the fourth embodiment is different. The row plate 5 is a circular plate having one window-shaped plate fixed to the inside of the oblique plate ring 24 and having a window-like void penetrating larger than a semicircle having the chord side surface 23 as a side. The slanting plate ring 24, in which connecting elements corresponding to the hinge joint 19 elements provided at both ends of the intermediate shaft 4 are located on the side of the points Ka and Kb, respectively.
The intermediate shaft 4 of the rotary piston 3 is fitted into the window of the oblique plate 5 and the hinge joints 19 are formed by the both pieces of the oblique plate 5, so that the oblique plate 5 and the rotary piston 3 are opposed to each other. And are intersected with the intersecting secant K as an axis of connection so as to be slidable in the ± θ angle range.

After all, the slanting plate 5 on the S-circle closes the inner walls 7a, 7a of both concave surfaces of the rotary piston housings 1a, 1a, and the half-moon operation of the constant volume space forming a hemisphere on both sides of the slanting plate 5. The chambers Ha, Ha are formed and the half-moon shaped operating chambers Ha, H
Each of a is formed in one of the working chambers A and D or B and C that form a comb shape in which the rotary piston 3 on the R circular surface changes volume in inverse proportion on the same plane. A suction hole In and a discharge hole Out for the working fluid are provided at appropriate positions on the wall of the housing 1 facing the half-moon shaped working chamber Ha. In this embodiment as well, the rotation in the direction of the arrow given to the input shaft 2 is as described above. Since the rotary piston 3 and the skew plate 5 which are transmitted to the pin joint joint 16 and are paired with each other are cooperatively rotated, and the volume of the working chambers A and D or B and C is increased or decreased in the operation thereof, the volume is increased. When this is done, the working fluid is sucked in from the suction hole In, and when it is reduced, the working fluid is discharged from the discharge hole Out.

[0098]

[Embodiment 5] This embodiment shown in FIG.
2 is a configuration of two comb-shaped working chambers A and D or B and C that are arranged in the housing 1 in the axial direction similarly to the configuration of the above, and is based on the configurations of the second embodiment and the common aspect 2. is there. It should be noted that, in order to restrain the phase of the skew plate 5, the orbital gap 9 of the orbiting groove provided in the inner wall of the housing 1 in the above-mentioned fourth embodiment is surrounded by the outer peripheral surface of the skew plate 5 in the same manner as in the second embodiment. The orbital ring 10 of the ring body which fits the orbital bearing 25 of the groove provided is fixedly protruded and fixed to the inner wall surface 7 of the housing 1 on the S circle surface. In this embodiment as well, the pin joint joint is attached to the portion of the ball center O. The input shaft 2 having 16 shaft centers 17 is fitted and supported by the main bearings 8 at the points P and P.

On the other hand, the rotary piston 3 has both arcuate surfaces 14, 14 on the same plate surface and both spherical arc surfaces 1 which are in contact with the spherical inner wall 7.
3, 13 and the arcuate surfaces 14, 14 between the intermediate shaft 4
Is a circular plate in which at least the central portion is interleaved in a semi-embedded manner, the skew plate 5 is a substantially semi-circular plate in which at least both sides of the intermediate shaft 4 are attached to one arcuate plate, or As shown in FIG. 16, the intermediate shaft 4 is a circular plate having both sides of the intermediate shaft 4 attached to the arcuate plate and the opposite sides of the arcuate plate are also connected in an arch shape so as to have a circular outer peripheral surface. Similar to the second and third embodiments, the four pillars are fixed to the rotary piston 3 at the central portion of the three divisions as the piston intermediate shaft 4a, and at both side portions to the oblique plate 5 as the oblique plate intermediate shafts 4b and 4b. , The hinge pin receiver 2 that fits the hinge pin at the joint part
The hinge joints 19 of 0, 21, 20, 21 are composed and connected.

After all, the inner wall surface 7 of the housing 1 forming the spherical surface G
The inside is formed in both half-moon-shaped working chambers Ha, Ha of the constant volume space by concave inner walls 7a, 7a facing each other with the orbital ring 10 of the inner projecting as a boundary, and the slanting plate 5 on the S circle surface, Each of the half-moon-shaped working chambers Ha, Ha is formed in a comb-shaped working chamber A, D, or B, C in which the rotary piston 3 on the R circular surface changes volume inversely proportionally on both sides on the same plane.

[0101]

Sixth Embodiment In this embodiment, the race ring 10 fixed to the inner wall surface 7 of the housing 1 in the fifth embodiment is constructed as a movable part in the housing 1. That is, this embodiment shown in FIG. 17 based on the configurations of the third embodiment and the common mode 2 is configured by replacing the fixed raceway ring 10 in the fifth embodiment with the movable raceway ring 6. A control device CA is attached to the movable orbital ring 6 so that the tilt angle (0 to ± θ) of the skew plate 5 can be freely changed.

That is, similar to the construction of the third embodiment, the raceway ring shafts 11, 11 of the raceway ring 6 are supported by the raceway ring bearings 12, 12 provided on the wall of the housing 1 on the points e, e side, and When a control device CA that controls the inclination of the skew plate 5 is attached to the orbital ring shafts 11 and 11 and is interlocked, the control device CA causes the tilt angle (0 to ± 0) of the skew plate 5 according to the discharge pressure of the pump. θ) is automatically changed and the stroke of the rotary piston 3 is changed to change the displacement volume of each working chamber A, D or B, C in one rotation of the shaft to secure the discharge amount according to the discharge pressure. To do.

[0103]

[Embodiment 7] This embodiment shown in FIGS. 18 and 19 has two working chambers A and B or two working chambers C which are vertically aligned with the shaft based on the construction of the first embodiment and the common mode 3. , D to operate. That is, in this embodiment, the inside of the housing 1 from the S-circle surface is defined by one cut plane parallel to the S-circle surface aa shown in FIG. The slanting plate housing 1b is formed into a large concave space, and the slanting plate housing 1b is divided into a hemispherical rotary piston housing 1a having a concave inner wall 7a facing the concave inner wall 7a. In the housing 1 configured as described above, the rotary piston 3 is a substantially semi-circular plate in which an arc-shaped plate and four intermediate shafts are combined,
The slanting plate 5 also has one of the two plate surfaces as a forming surface of the working chamber Fu, Fu, and the working chamber Fu, Fu forming surface faces the plate surface of the rotary piston 3 so that they can be interlocked with each other.

Therefore, the concave space portion of the oblique plate housing 1b is formed on the inner peripheral surface of the circle concentric with the Y axis as the orbital gap 9 for rotatably restraining the oblique plate 5. In this embodiment, Also, the main bearings 8 and 8 are provided through the rotary piston housing 1a wall and the skewed plate housing 1b side wall, which are opposed to each other on the X axis, and the main bearings 8 and 8 of the pin joint joint 16 are located at the ball center O position. The input shaft 2 having the shaft center 17 is supported. On the other hand, the rotary piston 3 of a semi-circular plate is provided with connecting elements of the hinge joint 19 on the points Ka and Kb at both ends of the intermediate shaft 4 as in the configuration of any of the above-mentioned embodiments, and the R-circle. A piston through hole 15 is opened along the surface, and a piston pivot 18 of a pin joint joint 16 element is provided at a ball center O position in the piston through bore 15 and is provided at the axial center 17 of the input shaft 2. Pivot.

The skew plate 5 has two arcuate surfaces 22 and 22 in which the strings are opposed to each other on the same plate surface, and both arcuate surfaces 2 thereof.
A semi-cylindrical concave chord side surface 23 formed in a groove-shaped concave portion that engages between the chord sides 2 and 22 so as to slidably contact the intermediate shaft 4 pillar;
A circular plate having an outer sliding contact surface 27 in which the back surfaces of both arcuate surfaces 22 and 22 are formed on the same rotation surface is larger than the circular plate diameter, and is annularly fitted to the raceway gap 9 so as to be rotatable and slidable. Is a circular plate united with the slanted plate ring 24 of FIG. 1, and the slanted plate through hole 26 for inserting the input shaft 2 is opened from the center of the chord side surface 23 to the outer sliding contact surface 27 to form the piston through hole 15 Intermediate shaft 2
The hinge joints 1 at both ends of the intermediate shaft 4 are joined to the openings, and on both opposite sides of the skew plate ring 24 at the points Ka and Kb.
A connecting element corresponding to 9 elements is provided. Then, insert the intermediate shaft 4 pillars into the chord side surface 23 of the skew plate 5,
The slant plate 5 and the rotary piston 3 are separated by a hinge joint 19 ±
When the θ angle range is slidably connected, the rotary piston 3
Is accommodated in the concave inner wall 7a of the rotary piston housing 1a with the spherical arc surface 13 being held in an improperly separated state, and the oblique plate ring 24 of the oblique plate 5 is also freely rotatable in the orbital space 9 of the oblique plate housing 1b. It is stored in a proper fitting state.

In this embodiment, the skew plate 5 on the S-circle closes the concave inner wall 7a of the rotary piston housing 1a to form a semi-spherical half-moon shaped working chamber Ha of a constant volume space. The half-moon-shaped working chamber Ha is formed into two working chambers A and B or C and D having a comb shape in which the rotary piston 3 on the R circular surface changes volume inversely. A suction hole In and a discharge hole Out for the working fluid are provided at appropriate positions of the housing 1 facing the half-moon shaped working chamber Ha. The rotation in the direction of the arrow given to the input shaft 2 causes the rotary piston 3 and the skew plate 5 to cooperatively rotate via the pin joint joint 16, and accordingly the working chambers A and B or C and D. Is increased or decreased, the working fluid is sucked from the suction hole In when the volume is increased, and the working fluid is discharged from the discharge hole Out when the volume is decreased.

[0107]

[Embodiment 8] In this embodiment, a fixed shaft is attached to the slant plate 5 for operation in place of the slant plate through hole 26 penetrating the center of the slant plate 5 in the construction of the seventh embodiment. . That is, as shown in FIG. 20, in contrast to the configuration of the seventh embodiment, in which the input shaft 2 has both side shaft necks supported by the main bearings 8 provided on the rotary piston housing 1a wall and the slant plate housing 1b wall. The input shaft 2 is configured so that the shaft column is attached only to one side of the shaft center 17, and is supported by the main bearing 8 provided on the wall of the rotary piston housing 1a. On the contrary, the shaft hole 26 is not formed, and conversely, a handle-shaped round bar is fixed to the center of the outer sliding contact surface 27 as the skew plate shaft 28, and the skew plate housing 1b is attached to the skew plate shaft 28. A slanted plate bearing 29 is provided in the center of the wall to deal with this.

In this case, the extension axis straight lines of the input shaft 2 and the skew plate shaft 28 are made to coincide with the X and Y axis lines intersecting at an angle θ on the spherical center O of the concave inner wall 7a of the housing 1. However, a bearing is pierced in each of the housing 1 walls on the X and Y axes that are opposite to each other, and one of them is a main bearing 8 that penetrates the rotary piston housing 1a wall on the X axis as the main bearing 8 of the input shaft 2. The shaft neck is supported, and the other is supported by inserting the skew plate shaft 28 as a skew plate bearing 29 that penetrates the wall of the skew plate housing 1b on the Y axis. In other words, also in this embodiment, the input shaft 2 and the skew plate 5 rotate on a rotational axis that is oriented at an angle θ, and the rotation of the input shaft 2 and the skew plate 5 increases with the rotation. The rotating piston 3 (rotating shaft L), which is supported in a restricted direction, makes a conical motion along the conical locus U.

[0109]

[Embodiment 9] This embodiment shown in FIG.
2 in the direction perpendicular to the axis in the housing 1 in the same manner as
This is an embodiment in which working chambers A and B or C and D are formed, and is based on the configurations of the second embodiment and the common aspect 3. In addition, this embodiment is different from the seventh embodiment in that
For the raceway 9 of the concave cavity of the housing 1 which restrains the phase of the skew plate 5, the same ring as the raceway ring 10 mounted in the above-mentioned Examples 2 and 5 is fixed to the inner wall surface 7 of the housing 1 on the S-circle. .

In this case, the rotary piston 3 is a semi-circular plate in which the arcuate plate is fixed to the arcuate chord side at least the central portion of the cylindrical intermediate shaft 4 in an integral structure, and the oblique plates 5 are the same. A circular plate formed by the two arcuate surfaces 22 and 22 on the plate surface and the outer sliding contact surface 27 on the back surface of the both arcuate surfaces 22 and 22 including the rotating outer peripheral surface has an intermediate shaft between the arcuate surfaces 22 and 22. Since it is a circular plate in which at least both side portions of 4 are fixed, the intermediate shaft 4 column is divided into at least 3 parts like the case of the above-mentioned Embodiments 2 and 5, and the central portion thereof serves as the piston intermediate shaft 4a. It is fixed to 3 and both sides are the intermediate shaft 4 of the skew plate.
hinge pins and hinge pin receivers 20 and 21, which are fixed to the slanting plate 5 as b and 4b, and are fitted and fitted to each other at their joints.
The slant plate 5 that connects and connects the hinge joints 19 of 20 and 21 and includes the bottom surfaces on the circumscribing sides of both the slant plate intermediate shafts 4b and 4b.
The orbital ring 10 is rotatably fitted in the orbital bearing 25 of the groove formed around the outer peripheral surface of the.

After all, the half-moon-shaped working chamber Ha is formed in the housing 1 by incorporating the oblique plate 5, and the half-moon-shaped working chamber Ha has two comb-shaped working chambers A whose volume is inversely proportionally changed by the rotary piston 3. B or C and D are formed, and the suction hole In and the discharge hole Out are formed at appropriate positions on the upper wall of the housing 1. The rotation in the direction of the arrow to be given is the rotation piston 3 and the skew plate 5. To increase or decrease the volume of the working chambers A and B or C and D, suck the working fluid from the suction hole In when the volume increases, and from the discharge hole Out when the volume decreases. Exhale working fluid.

[0112]

[Embodiment 10] In this Embodiment 9, the orbital ring 10 fixed to the inner wall surface 7 of the housing 1 is made independent as a movable part in the housing 1.
Further, based on the configuration of the common mode 3, a control device CA is newly provided so that the tilting angle (0 to ± θ) of the skew plate 5 can be freely changed.

That is, the tenth embodiment shown in FIG.
Similar to the configurations in the above-mentioned third and sixth embodiments, the orbit ring 6 which is movable in the inner wall surface 7 of the housing 1 which fits the orbit receiver 25 of the oblique plate 5 and supports the oblique plate 5 is mounted. The orbital ring shafts 11 and 11 attached to the opposite sides of 6 are rotatably supported by inserting the orbital ring bearings 12 and 12 provided on the wall of the housing 1 on the point e, e side, and to the orbital ring shafts 11 and 11. Skew board 5
The control device CA for controlling the inclination of is attached and interlocked. That is, the controller CA automatically changes the tilting angle (0 to ± θ) of the skew plate 5 according to the discharge pressure of the pump, and the shafts 1 of the respective working chambers A and B or the shafts 1 of C and D. The displacement volume during rotation is changed to secure a discharge amount according to the discharge pressure.

[0114]

[Embodiment 11] The embodiment 8 shown in FIG.
Working chambers A and B arranged in the direction perpendicular to the axis, as in the configuration in FIG.
Alternatively, the oblique plates are arranged in C and D, but the oblique plate housing 1b is formed in the orbital space 9 of a concave void larger than the S-circle diameter in the structure of the eighth embodiment. The peripheral wall surface corresponding to the housing 1b is also formed into a spherical surface G, and the oblique plate 5 is formed in the peripheral wall surface so as to be accommodated therein.

That is, in this embodiment, the main bearing 8 on the X axis is provided on the wall of the housing 1 having the inner wall surface 7 having the spherical surface G on the entire surface.
And a skewed plate bearing 29 on the Y-axis located on the opposite side thereof are provided so as to penetrate therethrough, and the input shaft 2 is fixed to the shaft center 17 in the same manner as in the configuration of the above-described eighth embodiment. Is supported by inserting a shaft neck into the main bearing 8, and the rotary piston 3 is fixed to the central portion of the intermediate shaft 4 which is divided into at least three parts on the arc-shaped plate in the same manner as in the embodiments 9 and 10 above. It is a semicircular plate.

The point skew plate 5 has two arcuate surfaces 2 on the same plate surface.
2, 22 and a double arcuate surface 2 that is in sliding contact with the inner wall surface 7 of the spherical surface G
2 and 22, the outer peripheral sliding contact surface 27 of the outer peripheral surface is included, and both sides of the intermediate shaft 4 divided into at least three parts are fixed between both arcuate surfaces 22 and 22, and the outer peripheral sliding contact surface 27 center Is a circular plate having a handle-shaped skewed plate shaft 28 protruding from the handle-shaped slanting plate bearing 28 for constraining the skewed plate 5 main body to the rotation of the stationary axis. Also in this embodiment, when the rotation in the direction of the arrow is given, the volume of the working chambers A and B or C and D increases or decreases, and when the volume increases, the working fluid is sucked from the suction hole In, and the volume decreases. In doing so, the working fluid is discharged from the discharge hole Out.

[0117]

[Embodiment 12] In the embodiment of FIG. 24, the portion of the skewed plate bearing 29 mounted and formed at the fixed position of the housing 1 in Embodiment 11 is made movable only in the plane direction passing through both the X and Y axes. By changing the phase of the skew plate shaft 28, the tilting angle (0 to ± θ) of the skew plate 5 can be arbitrarily changed.

That is, the housing 1 wall through which the skew plate shaft 28 penetrates on a plane passing through both the X and Y axis lines is opened at least within a range of ± θ angle with respect to the X axis line, and the skew plate axis is provided at the open portion. Although not shown, the skewed plate bearing 29 in which 28 is inserted is mounted, and the controller CA for controlling the movement of the skewed plate bearing 29 within the range of ± θ angle with respect to the X axis is set at a point e on the Z axis. , E are attached to the fulcrum to interlock. Eventually, the control device CA automatically changes the tilting angle (0 to ± θ) of the skew plate 5 according to the pump discharge pressure, so that each working chamber A,
The displacement volume in one rotation of the shaft B or C, D is changed to always secure the discharge amount according to the discharge pressure.

[0119]

Embodiments Common to Embodiments 1 to 12 Although not shown in any of the above embodiments, particularly in a compressor, a valve such as a check valve may be installed in the discharge hole Out of the compressor.

[0120]

Among the conventional fluid pumps and compressors, the reciprocating piston pump and the reciprocating piston compressor which are used at high pressure and high speed and are most versatile among them have a basic structure including a cylindrical cylinder and a piston. There are many problems in the basic structure and operation as described above.

That is, the reciprocating piston pump and the compressor have a large number of parts, have a complicated structure, require a special material, and require precision machining. In addition, the reciprocating mechanism and suction / discharge valves often suffer frictional wear and failures, and the stroke volume (displacement volume) is small relative to the volume of the entire pump, and the size of the pump body is large. Furthermore, there are noises and vibrations during operation, and careful attention is required for long-term use, disassembly, and assembly.

On the other hand, the spherical rotary piston pump and compressor of the present invention show a completely different shape from the conventional piston pump and compressor including gears, vanes, etc., and the basic structure is spherical or spherical. . This spherical and spherical structure is basically strong against impact load and thermal stress and is robust, and the structure of the combination of the spherical body and two circular pistons (rotating piston 3 and skew plate 5) housed in the spherical body is When the pressure becomes high, there is little leakage from the discharge side inside the pump to the suction side at the low pressure side, or inside the housing, that is, the volume efficiency is extremely good and the working chamber Fu space with high sealing performance is formed and maintained. To be done.

In the spherical rotary piston pump and compressor of the present invention, the rotation given to the input shaft 2 rotates the rotary piston 3 via the pin joint joint 16, and the hinge plate 19 also causes the skew plate 5 to rotate. . Then, the rotary piston 3
And the skew plate 5 are widened to expand the working chamber Fu space closed by the arcuate surfaces 14 and 22 of the rotary piston 3 including the inner wall surface 7 of the housing 1 and the intermediate shaft 4 and the skew plate 5. Then, the expanding working chamber Fu space forms a vacuum state to suck the working fluid. Then, with the rotation, the arcuate surface 14 of the rotary piston 3 changes with each rotation, and the oblique plate 5 arcuate surface 22
One reciprocating movement is performed with respect to each other, and the reciprocating movement is repeated to continuously suck and discharge the working chamber Fu space.

As described above, in the spherical rotary piston pump and compressor of the present invention, the rotational force applied to the input shaft 2 directly spreads the space between the rotary piston 3 and the skew plate 5 to perform a pumping action. It has structural features. Therefore, in addition to conventional reciprocating piston pumps and reciprocating compressors, there are no factors that cause various problems such as inertial force due to linear reciprocating motion of pistons, and there is no extra space, so it is essential. It is composed of space and simple parts, so there is no waste of space and complexity, and it is extremely small and lightweight compared to other pumps and compressors with the same displacement. Moreover,
There is no element of frictional wear such as reciprocating piston pump and compressor, especially uneven wear component, and it is not always necessary to install suction and discharge valves. If pressure oil is supplied to the suction side of the hydraulic pump, the hydraulic pump can be used as it is as a hydraulic motor of an actuator that operates in the opposite manner.

Further, the total efficiency (pump efficiency) represented by the product of the volumetric efficiency and the mechanical efficiency is generally the highest in the conventional pumps, but in comparison with that, it is basically an aggregate of circles. A certain fluid pump of the present invention, the compressor, as described above, the sliding contact surface is a circle, which is extremely advantageous for sealing and has little leakage, and the proportion of the actual discharge amount that decreases as the pressure becomes high shows a large volume efficiency, In addition, the rotating piston with no jerky effect is excellent in mechanical efficiency indicating the ratio of effective shaft input, and shows high pump efficiency. Alternatively, even when the speed is changed by a DC motor or an engine (internal combustion engine), the self-priming ability is excellent in the low speed and high speed regions, and almost no noise or vibration is generated, and continuous operation is performed especially at a high pressure level. In addition to being possible, continuous operation is also possible at high rotational speeds and high rated pressure and rated rotational speed levels.

As described above, since the spherical rotary piston pump and compressor of the present invention have a spherical structure, they are rich in rigidity and durability, have a simple and clear mechanism, are small and lightweight, are inexpensive, and have a discharge pressure. Even if it changes, the discharge amount does not change much, and the pulsation of the discharge amount can be reduced by increasing the number of working chambers Fu. It is a high-performance fluid pump that has high mechanical efficiency and volumetric efficiency and withstands high-pressure and high-speed use. , A compressor.

[Brief description of drawings]

FIG. 1 is a partial vertical perspective view of a basic figure showing the principle of the present invention.

FIG. 2 is a perspective view showing an angle change of a basic figure.

FIG. 3 is a perspective view showing an angle change of a basic figure.

FIG. 4 is a perspective view showing an angle change of a basic figure.

FIG. 5 is a perspective view showing an angle change of a basic figure.

FIG. 6 is a perspective view showing an angle change of a basic figure.

FIG. 7 is a perspective view showing a change in angle of a basic figure.

FIG. 8 is a perspective view showing a change in angle of a basic figure.

FIG. 9 is a side view showing the first embodiment of the present invention.

FIG. 10 is an exploded perspective view of a partial cross section of FIG.

FIG. 11 is a side view showing a second embodiment of the present invention.

12 is an exploded perspective view of a partial cross section of FIG.

FIG. 13 is a side view showing a third embodiment of the present invention.

14 is an exploded perspective view of a partial cross section of FIG.

FIG. 15 is a side view showing a fourth embodiment of the present invention.

FIG. 16 is a side view showing a fifth embodiment of the present invention.

FIG. 17 is a side view showing a sixth embodiment of the present invention.

FIG. 18 is a side view showing a seventh embodiment of the present invention.

19 is an exploded perspective view of a partial cross section of FIG.

FIG. 20 is a side view showing an eighth embodiment of the present invention.

FIG. 21 is a side view showing the ninth embodiment of the present invention.

FIG. 22 is a side view showing Embodiment 10 of the present invention.

FIG. 23 is a side view showing an eleventh embodiment of the present invention.

FIG. 24 is a side view showing an twelfth embodiment of the present invention.

FIG. 25 is a partial vertical sectional side view of (a), (b), (c), (d), (e), and (f) showing the operation and the volume change of the working chamber space in the present invention.

FIG. 26 is a continuation of FIG. 25, showing the operation and the volume change of the operation chamber space in the present invention (g) (h) (i) (j) (k).
(L) Each partial longitudinal side view.

FIG. 27 is a schematic front view showing the operation progress of the intake and discharge strokes in the present invention.

[Explanation of symbols]

G spherical surface O spherical center of spherical surface r radius of spherical surface G X X-axis (mounting axis of input shaft) Y Y-axis (formation axis of S-circle, rotation axis of skew plate) θ θ angle (X-axis and Y-axis Intersection angle on the acute angle side with) P P point (point where X axis intersects spherical surface G) Q Q point (point where Y axis intersects spherical surface G) U Conical locus U (bottoms of points P and Q, spherical center O Conical locus with vertices) M M axis (vertical axis of X axis, connecting axis of pin joint joint) Z Z axis (straight line orthogonal to both X and Y axes, orbit ring forming axis) ee point (Z The point where the axis intersects the spherical surface G) R R circle surface (horizontal circle surface on X axis line) S S circle surface (vertical circle surface on Y axis line) L L axis line (rotation axis line of R circle surface) K K axis line (R Intersecting secant between circle surface and S circle surface) Ka One end point of both ends of K axis Kb The other end point of both ends of K axis Ha Half-moon shaped space, half-moon shaped working chamber u Comb-shaped space, comb-shaped working chamber In suction hole, suction hole Out discharge hole, discharge hole CA Control device A for changing the inclination of the skew plate A space A, comb-shaped working chamber A B space B, comb-shaped working chamber B C space C, comb-shaped working chamber C D space D, comb-shaped working chamber D 1 housing 1a rotary piston housing 1b skew plate housing 2 input shaft 3 rotary piston 4 intermediate shaft 4a piston intermediate shaft 4b skew plate intermediate shaft 5 diagonal Row plate 6 Orbital ring 7 Inner wall surface, spherical inner wall 7a Rotating piston housing concave inner wall 8 Main bearing 9 Housing orbital gap 10 Housing orbital ring 11 Orbital ring shaft 12 Orbital ring bearing 13 Rotating piston spherical arc surface 14 Rotating piston Bow-shaped surface 15 Piston through hole 16 Pin joint joint 17 Shaft center 18 Piston center 19 Hinge joint 20 Hinge pin 21 Hinge pin receiver 22 Bow-shaped surface 23 of skew plate Chord side 24 oblique plate ring 25 orbits receiving 26 outer sliding surface 28 oblique plate axis 29 oblique plate bearing the skew plate through shaft holes 27 oblique plate

─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) F04C 2/00 F04C 18/00

Claims (4)

(57) [Claims] 1. A housing (1) having a spherical surface on its inner wall surface.
In, the main bearing (8) is pierced through the wall of the housing (1) on a straight line passing through the spherical center (O) of the spherical inner wall (7), and the shaft neck of the input shaft (2) having a straight axis shape is rotated. The orbital gap (9) of the orbiting groove on the inner wall surface of the housing (1) on the vertical plane of the axis which is freely inserted and has an angle (θ) on the input shaft (2) and intersects at the spherical center (O). In the housing (1), a straight line that is orthogonal to the input shaft (2) and the spherical center (O) is used as a connecting axis in the housing (1) at least an angle (θ × 2) in the horizontal direction on the input shaft (2). Of the spherical arc surface (1
3) and the spherical arc surface (13) is an arc of an arc, and a cylindrical intermediate shaft (4) is united on the chord side to form an arc surface (1
4) A substantially plate-shaped rotary piston (3) having an input shaft (2)
Is pivotally connected to a portion of the ball center (O) of the same, and in the housing (1) of the intermediate shaft (4), the rotary piston (3) intersects with the hinge in a hinge shape, and the outer periphery of the edge portion is formed into a ring shape. The slanted plate ring (24) is the orbital space (9).
The pin and the pin receiving hole are provided to the bottom surface of the intermediate shaft (4) and the opposite side portions of the slanting plate ring (24) facing the bottom surface of the intermediate shaft (4). A slanting plate (5) of a circular plate having a connecting element, which is slidably connected to each other in at least an angle (θ × 2) range and has an arcuate surface (22) on the plate surface, is provided. (5) closes the spherical inner wall (7) of the housing (1) to form a half-moon shaped working chamber (Ha) in a hemispherical space, and the rotary piston (3) combs the half-moon shaped working chamber (Ha). The suction hole (I) is formed in the comb-shaped working chamber (Fu) in the shape space, and is exposed to the comb-shaped working chamber (Fu).
n) and a discharge hole (Out) are appropriately provided, a spherical rotary piston pump and a compressor. 2. A housing (1) having a spherical surface on its inner wall surface.
In, the main bearing (8) is pierced through the wall of the housing (1) on a straight line passing through the spherical center (O) of the spherical inner wall (7), and the shaft neck of the input shaft (2) having a straight axis shape is rotated. A ring shape around the circumference of the housing (1) inner wall surface (7) on the vertical plane of the axis that is freely inserted and has an angle (θ) on the input shaft (2) and intersects at the spherical center (O) Of the orbital ring (10) is projected, and a straight line that intersects the input shaft (2) and the spherical center (O) at right angles is used as a connecting axis in the housing (1) at least horizontally on the input shaft (2). A spherical arc surface (1) which oscillates within a range of an angle (θ × 2) and whose outer peripheral surface is in sliding contact with the spherical inner wall (7).
3), a substantially plate-shaped rotary piston (3) having an arcuate surface (14) on the plate surface is pivotally connected to the spherical center (O) of the input shaft (2), and the housing (1) Inside the rotary piston (3)
Has a plate surface of an arcuate surface (22) intersecting with a hinge and a track bearing (25) of a groove that circulates on the outer peripheral surface thereof.
Is provided with a slanting plate (5) of a circular plate on which the orbital ring (10) is rotatably fitted, and a cylindrical intermediate shaft (at the intersection of the slanting plate (5) and the rotary piston (3) ( 4) is divided into cut surfaces parallel to both bottom surfaces, and each of them is divided into a slant plate (5) and a rotary piston (3).
, Which are fixed to each other so that they do not conflict with each other, and each of which has a connecting element for providing a pin and a pin receiving hole on each of the divided joint surfaces, is connected so as to be slidable at least within an angle (θ × 2) range, and then, the skewing is performed. The plate (5) closes the spherical inner wall (7) of the housing (1) to form a semi-lunar working chamber (Ha) of a hemispherical space, and the semi-lunar working chamber (Ha) is formed by the rotary piston (3). It is formed in the comb-shaped working chamber (Fu) in the comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
n) and a discharge hole (Out) are appropriately provided, a spherical rotary piston pump and a compressor. 3. A housing (1) having a spherical surface on its inner wall surface.
In, the main bearing (8) is pierced through the wall of the housing (1) on a straight line passing through the spherical center (O) of the spherical inner wall (7), and the shaft neck of the input shaft (2) having a straight axis shape is rotated. A ball center (O) is freely inserted and has an angle (θ) with its input shaft (2) and intersects with the axis of the ball (O) and the axis of the input shaft (2).
A circular hole of a race ring bearing (12) is provided on both opposite walls of the housing (1) on a straight line orthogonal to each other, and both race ring bearings (12) can be rotated within the spherical inner wall (7) of the housing (1). A handle-shaped race ring shaft (11) fixed to the opposing outer peripheral surface of a race ring (6) made of a circular body is rotatably supported, and the input shaft (2) is provided in the housing (1). And a spherical center (O) are used as a connecting axis to swing horizontally on the input shaft (2) at least within an angle (θ × 2) and the outer peripheral surface is brought into sliding contact with the spherical inner wall (7). Arc surface (1
3), a substantially plate-shaped rotary piston (3) having an arcuate surface (14) on the plate surface is pivotally connected to the spherical center (O) of the input shaft (2), and the housing (1) Inside the rotary piston (3)
Has a plate surface of an arcuate surface (22) intersecting with a hinge and a track receiver (25) of a groove that circulates on the outer peripheral surface thereof.
Is provided with a slanting plate (5) of a circular plate on which the orbital ring (6) is rotatably fitted, and a cylindrical intermediate shaft (at the intersection of the slanting plate (5) and the rotary piston (3) ( 4) is divided into cut surfaces parallel to both bottom surfaces, and each of them is divided into a slant plate (5) and a rotary piston (3).
Of each of the divided joint surfaces, each of which has a connecting element of a pin and a pin receiving hole, is slidably connected to each other in at least an angle (θ × 2) range, and the orbit For the ring (6), a control device (CA) for selecting the tilt angle of the orbital ring (6) with respect to the input shaft (2) from the angle 0 to an angle ± θ range is used. 11) mounted and interlocked, and then the slanting plate (5) closes the spherical inner wall (7) of the housing (1) to form a hemispherical working chamber (Ha) and its half-moon shape. The working chamber (Ha) is formed in the comb-shaped working chamber (Fu) of the comb-shaped space by the rotary piston (3), and is made to face the comb-shaped working chamber (Fu), and the suction hole (I) is formed.
n) and a discharge hole (Out) are appropriately provided, a spherical rotary piston pump and a compressor. 4. A housing (1) having a spherical surface on its inner wall surface.
In, the main bearing (8) is pierced through the wall of the housing (1) on a straight line passing through the spherical center (O) of the spherical inner wall (7), and the shaft neck of the input shaft (2) having a straight axis shape is rotated. The slanted plate bearing (2) is also fitted to the wall of the housing (1) on which the input shaft (2) is freely inserted and has an angle (θ) and intersects at the spherical center (O).
A circular hole 9) is provided on the opposite side of the main bearing (8), and a straight line orthogonal to the input shaft (2) at the spherical center (O) is connected to the input shaft (2) in the housing (1). A spherical arc surface (1) which oscillates in the horizontal direction at least within a range of an angle (θ × 2) and whose outer peripheral surface is in sliding contact with the spherical inner wall (7).
3) and a rotary piston (3) of a semi-circular plate formed on the plate surface and having an arcuate surface (14) is pivotally connected to the spherical center (O) of the input shaft (2), and the housing (1) ) Inside the rotary piston (3)
Has an outer peripheral surface that slidably contacts with the inner wall surface (7) of the housing (1) and an arcuate surface (22) on the plate surface, and the skew is provided in the center of the back surface side of the arcuate surface (22). Plate bearing (2
9) is provided with a diagonal skew plate (5) having a handle-shaped skew plate shaft (28) into which the skew plate (5) and the rotary piston (3) are inserted. At the intersection, a cylindrical intermediate shaft (4) is divided by a cut surface parallel to both bottom surfaces, and each of them is divided into a slant plate (5) and a rotary piston (3).
, Which are fixed to each other so that they do not conflict with each other, and each of which has a connecting element for providing a pin and a pin receiving hole on each of the divided joint surfaces, is connected so as to be slidable at least within an angle (θ × 2) range, and then, the skewing is performed. The plate (5) closes the spherical inner wall (7) of the housing (1) to form a semi-lunar working chamber (Ha) of a hemispherical space, and the semi-lunar working chamber (Ha) is formed by the rotary piston (3). It is formed in the comb-shaped working chamber (Fu) in the comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
n) and a discharge hole (Out) are appropriately provided, a spherical rotary piston pump and a compressor.