JP2002061586A - Spherical rotating piston pump and compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a spherical fluid pump with a rotating piston and a compressor. SOLUTION: To a housing 1 having a spherical inner wall 7, a rotating piston 3 of a rotating plate, which has an input shaft 2 inserted therethrough on a line passing through a spherical center O of the spherical inner wall 7, a spherical arc face 13 on the outer periphery face for slidably contacting the spherical inner wall 7 and a cylindrical intermediate shaft 4 integrally laid on the chord side of the spherical arc face 13 as a segment arc, is pivotally connected rockingly in a range of angle θ×2 with a line perpendicular to the input shaft 2 at the spherical center O, as a connecting base axis. On the intermediate axis 4 of the rotating piston 3, an oblique plate 5 is provided which is constrained by a track gap 9 formed by engraving the circumference of the inner wall 7 of the housing 1 on a plane with a line crossing the input shaft 2 at a angle θ to the spherical center O, as an axis, and which is connected across the rotating piston rockingly in a range of angle θ×2. Then, the spherical inner wall 7 of the housing 1 is formed into an interdigital operation chamber Fu with the oblique plate 5 and the rotating piston closed. A suction hole In and a discharge hole Out are provided facing the interdigital operation chamber Fu.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for sucking a fluid by evacuating a closed container by power supplied from the outside and sucking the fluid and applying pressure to the device, or as a device for compressing a gas. A rotating plate of a rotating piston 3 and a skew plate 5 which rotate in the spherical housing 1 is assembled, a space between the two rotating plates is formed as a vacuum portion, and the gap volume is changed. The present invention relates to a novel fluid pump for performing suction and discharge and a compressor.

[0002]

2. Description of the Related Art Conventionally, positive displacement pumps include circumscribed and inscribed gear pumps, balanced and unbalanced vane pumps, and piston pumps classified into axial, radial and reciprocating pumps. is there. Among them, as a hydraulic pump, most of the gear pumps are circumscribed gear pumps, the vane pumps are generally equilibrium type (constant discharge type) pumps, and the piston pumps are axial type pump oblique shaft type ( Typical examples are a vent axis type and a swash plate fixed type (swash plate type).

[0003] In the external gear pump, when a pair of meshing external gears rotate in a casing in which the outer circumference and the side face are in close contact with each other, a vacuum portion (space) is formed at a separated portion of the meshing of the gears, and a vacuum portion (space) is formed from the suction port. As the working fluid is sucked, the working fluid fills the tooth space of the suction port, and the working fluid accumulated in the tooth space is carried to the discharge port along the inner periphery of the casing by the rotation of the gear, and the gear at the discharge port is rotated. Are pushed out due to a decrease in volume due to the meshing of. This gear pump has a simple structure, a small number of parts, and a low manufacturing cost as compared with a piston pump or a vane pump. However, unlike the other two types of pumps, a variable discharge pump cannot be manufactured.

An equilibrium vane pump is a constant discharge pump, but can be used at a higher pressure than a non-equilibrium variable discharge vane pump. The balanced vane pump includes a cam ring fixed in a casing, a bushing pressed and fixed to a side surface of the cam ring, a rotor fixed to a drive shaft (input shaft) while being surrounded by the cam ring and the bushing, and Vane is built in and configured. The rotor has a groove cut in the radial direction and the vane slides freely in this groove, because the shaft, rotor and cam ring are concentric and the curve inside the cam ring is almost elliptical. The driven centrifugal force causes the vane to always adhere to the inside of the cam ring and rotate while performing suction / discharge operations. In this balanced vane pump, since each of the two suction / discharge ports is located at a symmetrical position, the pressure distribution is axisymmetric, and a load perpendicular to the axis is not applied.

[0005] In the axial type oblique-axis piston pump, a drive shaft and a rotating cylinder block are mounted in a pump housing at a fixed angle (20 to 30 degrees).
Cylinders are formed in the cylinder block at equal circumferential intervals in parallel with the axis, and a piston is inserted into each of the cylinders. Each of the pistons is connected to a drive shaft flange of a drive shaft via a piston rod and a piston rod end bearing at the end of the piston rod, and performs reciprocating motion in a cylinder block to perform a suction / discharge operation. 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.

Also, an axial type swash plate type (swash,
The plate pump) has a piston reciprocating in a cylinder block in the same manner as the above-described oblique-axis piston pump, but differs from the oblique-axis piston pump in that the cylinder block rotates when the shaft is driven, and Each of the pistons arranged therein slides on a tiltable swash plate via a shoe, and reciprocates with a stroke corresponding to the tilt of the swash plate to perform a suction / discharge pump action. .
This swash plate type piston pump has a smaller number of parts and a smaller size than a swash plate type piston pump, and has a simple mechanism and can be changed 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 a gear pump or a vane pump, they can be used at a high pressure with little leakage of working fluid, and are lightweight, compact and capable of high-speed rotation. Because it is possible, it can be directly connected to the prime mover or DC motor. Also,
Since the piston pump is of the plunger type, theoretically 9
It is a variable discharge rate type pump that can achieve 0% or more efficiency, can adjust the discharge amount steplessly with little pulsation of the discharge fluid and can reverse the discharge, and has low noise and long life. Although it is a long pump, it has the following disadvantages and problems.

[0008]

Problems of the prior art That is, a conventional fluid pump, especially a piston pump in a hydraulic pump, has a more complicated structure and a larger number of parts than a gear pump or a vane pump, requires special materials, and requires precision machining. High cost. Further, since this piston pump repeats a suction / discharge cycle by reciprocating motion of a piston or a plunger, the motion mechanism and the suction / discharge valve are often worn or broken, and mechanically or pulsating or pulsating. 5 to 9 pistons are inserted into the cylinder block in order to suppress the fluctuation of the discharge amount. The effective volume of the stroke volume is small with respect 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 oily deterioration due to long-term use, and to dust mixing during disassembly, assembly and operation.

In the vane pump, the vane and the rotor rotate between the cam ring and the bushing, so that the contact area is large. Roughness is often a problem, and the vanes are subject to repeated stresses with each revolution, which can lead to breakage. In addition, since the contact area is large, in order to improve the volumetric efficiency, it is necessary to determine the viscosity of the oil and reduce the gap, thereby limiting the viscosity of the hydraulic oil,
Care must be taken when maintaining oil because dust can be mixed into the oil used, or if the oil itself has deteriorated, it can significantly impair its function. That is, the gear pump is generally used at low horsepower of low pressure and low speed rotation except for a part, the piston pump of the axial type or the like is operated at high pressure and high speed rotation, and the vane pump has an intermediate performance between them. is there.

[0010] In addition, regarding the compressor, as the positive displacement compressor, there is a reciprocating compressor most widely used in addition to a vane compressor, a roots blower, a Nash pump and a screw compressor. The compressor body of the reciprocating compressor is divided into a reciprocating part for driving a piston, a container part such as a cylinder and a cylinder head, a suction valve / discharge valve, and a pipe and the like connected thereto. The reciprocation of the piston causes the piston to reciprocate via the connecting rod and the piston rod, and the reciprocating motion of the piston compresses the air (or gas) flowing from the suction port and generates high pressure and high temperature from the discharge port. It is to be ejected. This reciprocating compressor has a stronger structure and fewer failures than other compressors, and is relatively easy and efficient to handle and maintain.However, the structure is complicated, the number of parts is large, and the size is large.
The production cost is high, the vibration is large, and generally large works are required for foundation and installation. If the maintenance is poor, there is a danger of overheating and explosion or fire.

[0011]

SUMMARY OF THE INVENTION In view of the above-mentioned problems of the conventional fluid pump and compressor, a book comprising a spherical housing and a pair of rotary plates rotating therein. The fluid pump of the invention has a small pulsation of the working fluid (discharge oil) to be discharged, a small change in the discharge amount even if the discharge pressure changes, and a low pressure from the discharge side inside the pump when the pressure increases. It has little leakage on the suction side or inside the case, and exhibits high self-priming performance and high overall efficiency (pump efficiency) even in low-speed / high-speed ranges. Also, as a compressor, the rotating piston facilitates high-speed and high-pressure operation and exhibits high compression efficiency and mechanical efficiency, eliminating the need for multiple stages.
A completely new fluid pump with a basic spherical structure and various performances superior to conventional gear pumps, vane pumps, piston pumps, reciprocating compressors, etc. Is provided.

[0012]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention coaxially connects and intersects each other in a sealed housing 1 having a spherical inner wall surface 7 so that only hinge-like operation is possible. Two rotating plates, a rotating piston 3 and a skewing plate 5, are incorporated, and the rotating 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. When installed, the rotating piston 3
When the plate surfaces of the skew plate 5 and the skew plate 5 repeat approaching and separating 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 of the two approach and close each other. In the present invention, there are generally the following four solutions.

[0013]

A first aspect of the present invention is a housing 1 having a spherical surface on an inner wall surface. Of the input shaft 2 is rotatably inserted into the input shaft 2 and has an angle θ with the input shaft 2. 9 is cut.

In the housing 1, the input shaft 2 is provided.
And a straight line orthogonal to the spherical center O as a connection axis, and swings horizontally on the input shaft 2 at least in the range of an angle (θ × 2),
In addition, the outer peripheral surface is formed on a spherical arc surface 13 which is in sliding contact with the spherical inner wall 7, and the cylindrical intermediate shaft 4 is combined with the chord side having the arc surface 13 as an arc of an arc to form an arcuate surface 14 on the plate surface. Is pivotally connected to the spherical center O of the input shaft 2.

In addition, in the housing 1, a skewed plate ring 24 hingedly intersecting with the rotary piston 3 on the intermediate shaft 4 and having an annular outer periphery is rotatable in the raceway gap 9. And a connecting element for providing a pin and a pin receiving hole to each of both bottom surfaces of the intermediate shaft 4 and opposing opposite side portions of the oblique plate ring 24 which are in contact with the both bottom surfaces. The oblique plates 5 are circular plates that are connected to each other at least in an angle (θ × 2) range and that have an arcuate surface 22 on the plate surface.
Is provided.

Then, the inclined 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 half-moon shaped working chamber Ha is
Are formed in the comb-shaped operation chamber Fu in the comb-shaped space. Further, the suction hole In and the discharge hole Out are exposed to the comb-shaped working chamber Fu.
And a spherical rotary piston pump and a compressor provided as appropriate.

[0017]

As another solution, in a housing 1 having a spherical surface on an inner wall 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 so as to form a straight shaft. The shaft neck of the input shaft 2 in the shape of
In addition, a ring-shaped orbital ring 10 is protruded from a circumference of the inner wall surface 7 of the housing 1 on a vertical plane of an axis intersecting the spherical axis O at an angle θ with respect to the input shaft 2.

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

In addition, the housing 1 has a raceway bearing 25 of a groove which intersects the rotary piston 3 in a hinged manner and circulates around the plate surface of the arcuate surface 22 and the outer peripheral surface. A skew plate 5 of a circular plate into which the race ring 10 is fitted in a rotational sliding relationship is provided.

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

Then, the swash plate 5 closes the spherical inner wall 7 of the housing 1 to form a hemispherical working chamber Ha of a hemispherical space. It is formed in a comb-shaped working chamber Fu. Furthermore, a spherical rotary piston pump and a compressor are provided with a suction port In and a discharge port Out appropriately facing the comb-shaped working chamber Fu.

[0022]

Another solution is that in a housing having a spherical surface on an inner wall surface, a main bearing is provided in a wall of the housing on a straight line passing through a spherical center of the spherical inner wall, and a main bearing is penetrated. The input and output shaft 2 is rotatably fitted with the shaft and neck, and the input shaft 2 has an angle θ and intersects with the input shaft 2 at an angle θ. A circular hole of a race ring bearing 12 is provided on both opposite walls of the housing 1 on a straight line, and the race ring 6 is formed of a ring body rotatably provided in the spherical inner wall 7 of the housing 1. A handle-shaped orbital ring shaft 11 fixed to the diametrically opposed outer peripheral surface is rotatably supported.

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

In addition, the housing 1 has a track bearing 25 of a groove intersecting the rotary piston 3 in a hinge shape and orbiting on the plate surface of the arcuate surface 22 and the outer peripheral surface. The swash plate 5 of a circular plate into which the race ring 6 is fitted in a rotational sliding relationship is provided.

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

The orbital ring 6 has the input shaft 2
From the angle 0 to the angle ± θ
The control device CA for selecting any one of the ranges is
Attach to 1 and link.

Then, the swash plate 5 closes the spherical inner wall 7 of the housing 1 to form a hemispherical working chamber Ha of a hemispherical space, and the rotating piston 3 forms the semi-lunar working chamber Ha of the comb-shaped space. It is formed in a comb-shaped working chamber Fu. Furthermore, a spherical rotary piston pump and a compressor are provided with a suction port In and a discharge port Out appropriately facing the comb-shaped working chamber Fu.

[0028]

A further solution is to provide a housing 1 having a spherical surface on an inner wall surface, wherein 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 is rotatably inserted, and the wall of the housing 1 on the straight line which intersects with the input shaft 2 at an angle θ at the spherical center O is also formed in the circular hole of the oblique plate bearing 29. 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 spherical center O as a connection axis, and swings horizontally on the input shaft 2 at least in the range of an angle (θ × 2),
The outer peripheral surface is formed on a spherical arc surface 13 which is in sliding contact with the spherical inner wall 7, and the rotary piston 3 of a semicircular plate having an arcuate surface 14 on the plate surface is pivotally connected to the portion of the spherical center O of the input shaft 2.

In addition, the housing 1 has an outer peripheral surface which intersects the rotary piston 3 in a hinge-like manner and slides on the inner wall surface 7 of the spherical housing 1 and an arcuate surface 22 on the plate surface. A circular plate-shaped swash plate 5 having a skewing plate shaft 28 into which the skewing plate bearing 29 is rotatably inserted is provided at the center of the rear surface side of the surface 22.

At the intersection of the swash plate 5 and the rotary piston 3, a columnar intermediate shaft 4 is divided by a cut surface parallel to both bottom surfaces, and each of them is divided by the skew plate 5 and the rotary piston 3. Each of the divided joining surfaces is provided with a connecting element for providing a pin and a pin receiving hole to each other so as to be slidable at least in an angle (θ × 2) range.

Then, the swash plate 5 closes the spherical inner wall 7 of the housing 1 to form a hemispherical working chamber Ha of a hemispherical space. It is formed in a comb-shaped working chamber Fu. Furthermore, a spherical rotary piston pump and a compressor are provided with a suction port In and a discharge port Out appropriately facing the comb-shaped working chamber Fu.

[0033]

[Geometric configuration] The rotary piston pump and the compressor of the present invention are based on the points, lines,
There is a characteristic of the basic structure that is established on the surface geometrical figure. The structure of the present invention in its interrelated geometric figures will be described in detail below.

First, FIG. 1 shows an interrelation pattern defining the present invention. A housing 1 formed on an inner wall surface forming a spherical surface G having a radius r from a spherical center O has a spherical surface with an angle θ. The straight lines that intersect at the center O are defined as the X axis and the Y axis, and the X
Let P be the point where the axis intersects the spherical surface G, and let the Y axis be the spherical surface G
Is defined as Q, a point between the point P and the point Q is defined as a diameter of the bottom surface, and a conical trajectory of a conical cone having a vertex at the sphere O is defined as U. An axis straight line orthogonal to the axis is defined as an M axis, an axis straight line that intersects both the X and Y axes at right angles on the spherical center O is defined as a Z axis, and both points where the Z axis intersects the spherical surface G are defined as e and e. A large circular plane in a spherical surface G having a horizontal plane with its axis L as a rotation axis and a large circular plane in a spherical surface G having an axis L as a rotation axis, and a Y axis line as a vertical axis are formed through the spherical center O in the spherical surface G. A large circle plane is defined as an S-plane, an intersection line where the R-plane and the S-plane intersect at the spherical center O is defined as an axis K, and both ends of the intersection K are points K.
a, a point Kb, and the respective relationships among the point, the line, and the surface are set as described above.

If the X-axis and the Y-axis are regarded as fixed-position fixed axes, and the X- and Y-axes are simultaneously rotated, the S-circle, which is a vertical plane of the Y-axis, retains its phase. R circle surface with the axis L as the axis of rotation
It turns while rotating in the order of FIG. 3 through FIGS. 1 and 2 through FIG. 1 through FIG. Then, in the rotation by 90 degrees of the rotation, the rotation axis L of the R-circular surface revolves around the semicircle in FIGS. 1 to 3 on the X-axis and moves on the Y-axis. Further, in the rotation by 90 degrees, the remaining semicircular locus is drawn from the Y-axis line through FIG. 4 and returns to the X-axis line in FIG. That is, if the rotation axis L of the R-circle revolves (revolves) around the circumference of the conical trajectory U, the R-circle rotates 180 degrees, which is a half rotation, to change the front and back with the revolution.

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

When looking at the closed spaces A, B, C, and D surrounded 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, 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, and 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. In addition, the space D contracts when the space A expands, and the space C expands when the space B contracts. In a relationship. Therefore, the spaces A and B form a pair by changing the volume increase / decrease in inverse proportion to each other, and the spaces C and D also pair by changing the volume increase / decrease in inverse proportion to each other, and the spaces A and C and the space B
And D have a relationship opposite to the order in which the volume change is directly proportional to each other.

In each of the relations of points, lines and surfaces set in this manner, the housing 1 spherical inner wall 7 has a spherical surface G according to the above figure, and the input shaft 2 on the X axis passing through the spherical center O of the spherical surface G The main bearing 8 at the point P is inserted into the main bearing 8 to support the bearing. A pin joint joint 16 having the axis M as a base axis of the joint is formed on the R-circular surface of the geometric figure to form the input shaft 2.
And a skew plate 5 is placed on an S-circle surface with the Y-axis as the rotation axis. The rotating piston 3 on the R-circle and the skew plate 5 on the S-circle form an intermediate shaft 4 on the K axis and intersect with each other. Hinge joint 1 with axis
9 are combined and connected. Note that the space A in the geometric figure,
B, C, and D are two comb-shaped working chambers Fu, Fu, Fu, and Fu formed in the two half-moon working chambers Ha, Ha, respectively.
It is.

[0039]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the present invention, there is an embodiment based on the structure of each of the above-mentioned solving means 1 to 4. The various embodiments are described with respect to points, lines,
A description will be given below with reference to the drawings based on each relationship between the surfaces.

[0040]

[Embodiment 1] One of the embodiments is the configuration of the above-mentioned solution 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 inner surface 7 of the spherical surface. A main bearing 8 having a bearing hole is provided at a position P on the wall of the housing 1 through which the X-axis passes, and the main body 8 rotates the shaft and neck of the input shaft 2 having a linear shape with the X-axis as a rotation axis. Freely insert and allow bearing. Also, the inner wall of the housing 1 on the extension of the S-circle which is the vertical plane of the Y-axis crossing the spherical axis O at an angle θ with the input shaft 2 on the X-axis at an angle θ is formed in the raceway gap 9 of the orbital groove.

Then, on the R-circular surface in the housing 1,
A semicircular arcuate surface 14 is provided on the plate surface, and an outer peripheral surface is formed on the spherical arc surface 13 which comes into sliding contact with the spherical inner wall 7.
A substantially plate-shaped rotary piston 3 is disposed on the chord side of an arcuate surface 14 having an arcuate arc 3 and having a columnar intermediate shaft 4 with an axis K attached to the chord side. The rotary piston 3 and the input shaft 2 are connected to each other at an angle (θ) in the horizontal direction on the input shaft 2 with the M axis perpendicular to the X axis and the sphere O being the center axis of the connection.
The range of × 2) is combined with a pin joint joint 16 composed of a swingable pin and its pin receiver.

On the S-circular surface in the housing 1, an arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 is formed on a plate surface.
A skew plate 5 having a circular shape and having an outer periphery formed in an annular shape is fitted into the raceway gap 9 and is constrained to be rotatable about the Y axis. 3 on the intermediate shaft 4 so as to intersect with each other in a hinge shape.
The hinge 1 having the K-axis as the joint base axis with the two pieces of the pin and the pin receiving hole on the sides Ka and Kb of the two bottom surfaces of the pair and the opposite side portions of the oblique plate ring 24 which are in contact with the both bottom surfaces.
9, the rotating piston 3 is connected to the swash plate 5 so as to be able to slide at least in an angle (θ × 2) range.

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

[0044]

Second Embodiment Another embodiment is the configuration of the above-mentioned solution 2. That is, this embodiment 2 is shown in FIGS.
As shown in FIG. 21 and FIG. 21, in the housing 1 having the inner surface of the spherical surface G, 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 inner surface 7 of the spherical surface.
And the main bearing 8 is fitted with the shaft neck of the input shaft 2 having a linear shape with the X-axis as the rotation axis, and the main bearing 8 is supported. Also, the raceway ring of the ring is formed on the inner wall surface of the housing 1 on the periphery of the S-circumferential edge which is a vertical plane of the Y-axis crossing the input axis 2 on the X-axis at an angle θ at the spherical center O at the spherical center O. 10 is formed in a protruding manner.

Then, on the R-circular surface in the housing 1,
The spherical surface of the input shaft 2 is formed by arranging a substantially plate-shaped rotary piston 3 having an outer peripheral surface formed on a spherical arc surface 13 that comes into sliding contact with the spherical inner wall 7 and a plate surface formed on a semicircular arcuate surface 14. Heart O
Pivot to a position. The rotating piston 3 and the input shaft 2
The rotating piston 3 has a horizontal axis on the input shaft 2 at least at an angle (θ
A pin joint joint 16 is formed and connected to each other so as to be swingable in the range of × 2).

On the S-circular surface in the housing 1, an arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 is formed on the plate surface, and the same circumference of the outer peripheral surface is cut into a circular groove. A circular plate skewing plate 5 having the formed track bearing 25 is arranged so as to intersect the rotating piston 3 in a hinge-like manner.
The orbital groove of the raceway support 25 is fitted into the raceway ring 10 in a sliding contact relation, and is constrained to be rotatable about the Y axis.

At the intersection of the skew plate 5 on the S-circle and the rotating piston 3 on the R-circle, a columnar intermediate shaft 4 with its intersection line K interposed as an attachment axis is parallel to both bottom surfaces. And a skew plate 5 which is divided into a plurality of cut surfaces and which is fixed to the rotating piston 3 at a piston intermediate shaft 4a.
And a skew plate intermediate shaft 4b secured to the skewed plate intermediate shaft 4b, and a K axis line formed by a pin and a pin receiving hole at the joint between the piston intermediate shaft 4a and the skew plate intermediate shaft 4b. The rotating piston 3 is connected to the swash plate 5 so as to be able to slide at least in an angle (θ × 2) range by forming a hinge joint 19 serving as a joint base axis.

Then, the oblique plate 5 on the S-shaped surface closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form a semi-lunar working chamber Ha composed of a hemispheric constant volume space, and the half-moon is formed. The working chamber Ha is formed as a comb-shaped working chamber Fu in a comb-shaped space in which the volume of the rotating piston 3 on the R-shaped surface changes. Furthermore,
The suction hole In and the discharge hole Out are appropriately provided facing the comb-shaped operation chamber Fu of the half-moon-shaped operation chamber Ha.

[0049]

[Embodiment 3] Still another embodiment is the structure of the above-mentioned solution 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 and 14 and FIGS. 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 point P on the wall of the housing 1, and the shaft and neck of the input shaft 2 having a linear shape with the X axis as a rotation axis is fitted into the main bearing 8 to be supported.
A track ring bearing 12 having a Z-axis as a bearing axis is provided on both opposing walls of the housing 1 on points e and e on a Z-axis orthogonal to the spherical axis O at both the X-axis and the Y-axis. In addition, a handle-shaped orbital ring shaft 11 is fixed to each of the opposed outer peripheral surfaces to provide a ring-shaped orbital ring 6 rotatable within the inner wall surface 7 of the housing 1. The bearing is inserted into the race ring bearing 12 and is rotatably supported.

Then, on the R-circular surface in the housing 1,
A substantially plate-shaped rotary piston 3 having an outer peripheral surface formed on a spherical arc surface 13 which comes into sliding contact with the spherical inner wall 7 and a plate surface formed on a semi-moon-shaped arcuate surface 14 is disposed, and the spherical surface of the input shaft 2 is arranged. The rotary piston 3 and the input shaft 2 are connected to the center O position.
The rotating piston 3 has a horizontal axis on the input shaft 2 at least at an angle (θ ×
A pin joint joint 16 is formed and connected with both pieces to be able to swing in the range of 2).

The S-shaped surface in the housing 1 has an arcuate surface 22 corresponding to the arcuate surface 14 of the rotary piston 3 on the plate surface, and the same circumference of the outer peripheral surface is cut into a circular groove. A circular plate skewing plate 5 having a formed track bearing 25 is arranged to intersect the rotary piston 3 in a hinged manner.
Is engaged with the orbital ring 6 in a slidable relationship with the orbital groove of the orbital bearing 25 so as to be rotatable 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 columnar intermediate shaft 4 with the intersection K as an attachment axis is parallel to both bottom surfaces. It is divided into a plurality of cut surfaces, and is divided into a portion of a piston intermediate shaft 4a fixed to the rotary piston 3 and a portion of a swash plate intermediate shaft 4b fixed to the swash plate 5, and the piston At the joint between the intermediate shaft 4a and the swash 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. Are connected so that at least the angle (θ × 2) range can be slid.

The orbital ring 6 has a orbital ring 6 phase control device CA for freely changing the tilt angle of the orbital ring 6.
Is attached to and linked to the orbital ring 11, and the tilt of the orbital ring 6 about the orbital ring 11 on the Z axis is shifted from the angle 0 to the angle ± θ with respect to the X axis of the input shaft 2. The control device CA automatically selects any of the ranges.

Then, the sloping plate 5 on the S-circle surface closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form a semi-lunar working chamber Ha composed of a hemispheric constant volume space. The working chamber Ha is formed as a comb-shaped working chamber Fu in a comb-shaped space in which the volume of the rotating piston 3 on the R-circular surface changes. Furthermore,
The suction hole In and the discharge hole Out are appropriately provided facing the comb-shaped operation chamber Fu of the half-moon-shaped operation chamber Ha.

[0055]

[Fourth Embodiment] Still another embodiment is the configuration of the above-mentioned solution means 4. That is, in the fourth embodiment, as shown in FIGS. 23 and 24, in the housing 1 having the inner wall surface of the spherical surface G, on the point P side of the wall of the housing 1 through which the X axis passes through the spherical center O of the spherical inner wall 7. A main bearing 8 is penetrated, a shaft neck of a linear input shaft 2 having an X-axis as a rotation axis is inserted into the main bearing 8 and supported, and an angle θ is formed on the input shaft 2 on the X-axis. Also, a circular hole of the oblique plate bearing 29 is provided on the opposite side of the main bearing 8 on the wall of the housing 1 on the Y axis line intersecting with the ball center O.

Then, on the R-circular surface in the housing 1,
The input shaft 2 is provided with a semicircular plate rotating piston 3 having an outer peripheral surface formed on a spherical arc surface 13 in sliding contact with the spherical inner wall 7 and a plate surface formed on a semicircular arcuate surface 14. It is pivoted to the ball center O position. The rotating piston 3 and the input shaft 2 are X
The rotating piston 3 has a horizontal axis on the input shaft 2 at least at an angle (θ ×
A pin joint joint 16 is formed and connected with both pieces to be able to swing in the range of 2).

On the S-circular surface in the housing 1, there are 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 on the plate surface. And a skew plate 5 of a circular plate having a swash plate shaft 28 of a pattern-shaped circular column fixed to the center of the back surface side of the arcuate surface 22 is arranged so as to intersect the rotary piston 3 in a hinge-like manner. The skew plate 5 is rotatably supported by inserting a skew plate shaft 28 having a 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 columnar intermediate shaft 4 having its intersection line K as an attachment axis is parallel to both bottom surfaces. And a skew plate 5 which is divided into a plurality of cut surfaces and which is fixed to the rotating piston 3 at a piston intermediate shaft 4a.
And a skew plate intermediate shaft 4b secured to the skewed plate intermediate shaft 4b, and a K axis line formed by a pin and a pin receiving hole at the joint between the piston intermediate shaft 4a and the skew plate intermediate shaft 4b. The rotating piston 3 is connected to the swash plate 5 so as to be able to slide at least in an angle (θ × 2) range by forming a hinge joint 19 serving as a joint base axis.

Then, the oblique plate 5 on the S-circle surface closes the inner wall surface 7 forming the spherical surface G of the housing 1 to form a semi-lunar working chamber Ha composed of a hemispheric constant volume space, and the half-moon is formed. The working chamber Ha is formed as a comb-shaped working chamber Fu in a comb-shaped space in which the volume of the rotating piston 3 on the R-circular surface changes. Furthermore,
The suction hole In and the discharge hole Out are appropriately provided facing the comb-shaped operation chamber Fu of the half-moon-shaped operation 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, the half-moon-shaped working chambers Ha, Ha are formed on both sides of the swash plate 5, and each of the two half-moon-shaped working chambers Ha, Ha is provided with two circular plate rotating pistons 3. Each of the comb-shaped working chambers Fu, Fu, Fu,
Fu (spaces A, B, C, D). Common mode 2
(Two working chambers arranged horizontally with respect to the rotation axis). In the first to third embodiments, the half-moon-shaped working chambers Ha, Ha are formed on both sides of the swash plate 5, and the two half-moon-shaped working chambers Ha, Ha are formed.
Each of the Ha is formed in a comb-shaped working chamber Fu, Fu (spaces A, D or spaces B, C) by a hemispherical plate rotating piston 3. Common mode 3 (two working chambers arranged in a direction perpendicular to the rotation axis). In the first to fourth embodiments, the semi-lunar working chamber Ha is formed only on one of the two sides of the skewing plate 5, and the semi-circular working chamber Ha is formed by a semi-circular plate-like rotating piston 3 having two comb-like shapes. Working chamber Fu, Fu (space A, B or space C,
D).

In any of the above embodiments,
The practical range of the tilt angle θ created by crossing the X axis and the Y axis at the spherical center O is 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 the compressor according to the present invention having the above-described structure will be described with reference to the rotation interlock between the rotary piston 3 and the swash plate 5 and the resulting change in the volume of each working chamber Fu. Based on FIGS. 25 and 26, taking the first embodiment and the common mode 1 as examples, the mounting of the working fluid inlet / outlets In and Out, and the full 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 swash plate 5 in FIG. 25A are engaged with the pin joint 16 and the hinge 19 interposed therebetween, the input shaft 2 Is rotated by an electric motor or a prime mover such as an internal combustion engine, the rotating piston 3 is guided on the rotation plane of the swash plate 5 and turns the spherical center O of the inner wall surface 7 of the housing 1 which is the common center of the three members. A conical motion is made along the conical locus U as a center. That is, FIGS. 25 and 26 (a) to (l) show a half rotation (180
It shows the operation corresponding to (degrees) minutes.

The comb-shaped working chamber Fu shown in FIG.
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 skew plate 5, and the inner wall surface 7 of the housing 1 is inclined by the rotating piston 3 incorporated therein. 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 four intermediate shafts. 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.

In other words, if the rotary piston 3 which is a double-end piston is incorporated into each of the half-moon working chambers Ha, Ha formed at the double end by the skewing plate 5 and operated, the same half-moon working chamber is obtained. When the space on either side 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 other side contracts to reduce the volume, and the skew 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 the volume in inverse proportion to each other. Note that the two working chambers A and C, and B and D, which face each other with the swash plate 5 obliquely interposed therebetween, change in such a manner that their volumes always increase and decrease in direct proportion.

After all, the formation of the comb-shaped space is a gap between the plate surfaces of the rotating piston 3 and the swash plate 5 facing each other. Therefore, assuming that the gap between the plate surfaces is the working chamber Fu space, the approach between the plate surfaces of the rotating piston 3 and the skewing plate 5 given to each other is the contraction of the gap formed between the plate surfaces and the operation is performed. Reduction of the volume in the chamber Fu space, which corresponds to the operation of the reciprocating piston pump and the piston or plunger of the reciprocating compressor in the process of moving two dead points from bottom dead center to top dead center in the cylinder. . On the other hand, the separation of the rotating piston 3 and the swash plate 5 from each other gives rise to an increase in the space volume, and the reciprocating piston pump, the piston in the reciprocating compressor, or the plunger moves from the top dead center to the bottom dead center. This corresponds to the process of moving to the 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 and has a minimum volume, and the working chamber C at a symmetrical position of the working chamber A also has its working chamber gap contracted. The working chamber B, which shares the same semi-lunar working chamber Ha with the working chamber A, and the working chamber D, which shares the other half-moon working chamber Ha with the working chamber C, both have the smallest working volume. Has an upper limit volume. 25 (a), the rotating piston 3 is placed on the input shaft 2 in a 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 passage hole 15 are provided. And are in an overlapping state.

In this case, the rotating piston 3 swings in a plane direction on the input shaft 2 with the input shaft 2 as the amplitude base line.
5 horizontal equilibrium line of the rotating piston 3 passing through the center of 5 (axis L)
Are gradually deviated from the input shaft 2 and are biased, and the working chambers A and C have their working chamber spaces expanded in the order of FIGS. On the contrary, in the working chambers B and D, the plate surfaces of the rotary piston 3 and the swash plate 5 approach each other, and the working chamber spaces shrink, and their volumes are reduced.

Then, as shown in FIG. 26 (g), the rotating piston 3 moves by an opening angle (tilt angle θ) created between the axis of the input shaft 2 and the swash plate 5, which is caused by the input shaft 2 Of 90 degrees, and four working chamber spaces A, B, C,
Although the volume change of D becomes medium and the respective volumes become equal, if the operation proceeds further in the directions shown in FIGS. 26 (h) to 26 (k), the gaps between the working chambers A and C become smaller. Expands further to increase the volume, and conversely, further reduces the volumes of the working chambers B and D. That is, the rotating piston 3 in FIG.
Makes a half turn of 180 degrees, the front and back of the rotating piston 3 are switched as shown in FIG. 26 (l), and the working chambers A and C both expand the working chamber gap to have a maximum volume. Conversely, the working chambers B and D contract their volumes from the upper limit to the lower limit.

The volume change of each of the working chambers A, B, C and D from FIG. 25 (a) to FIG. 26 (l) corresponds to a rotation of 180 degrees, but the working chamber A in FIG. , C until the gaps of the working chambers B and D reach the lower limit, and the gaps of the working chambers B and D both reach the upper limit.
From (a), 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 a suction fluid In and a discharge hole Out are formed at appropriate positions in the housing 1 to supply a working fluid, and the above-described two-stroke cycle is repeated, the spherical rotary piston pump and compressor of the present invention can be provided. Operates as a fluid pump and compressor. At that time, especially for the compressor, the discharge holes Out
A valve such as a check valve (check valve) may be attached to the side.

[0071]

In the spherical rotary piston pump and compressor according to the present invention, the volume change of the comb-shaped working chamber Fu which alternates from the minimum to the maximum and from the maximum to the minimum corresponds to one rotation angle of the input shaft two rotation angles as described above.
It is performed every 80 degrees and has two strokes, a suction stroke and a discharge (compression) stroke, like a conventional reciprocating piston pump, compressor, or vane pump with a constant displacement. Is performed during 360 degrees of the shaft rotation, that is, during one rotation of the input shaft 2. Further, in the spherical rotary piston pump and the compressor of the present invention, the flow holes through which the fluid flows in and out of each of the working fluids of the liquid and the gas are discharged into the respective half-moon-shaped working chambers Ha and the discharge holes In. At least one hole Out is drilled at a position substantially opposite to the wall of the housing 1, in which case the inlet and outlet In and Out are located on a plane passing through both the X and Z axes shown in the geometric configuration. To the inner wall surface 7 of the housing 1.

FIG. 27 shows the operation of the spherical rotary piston pump and compressor according to the present invention. The respective steps of suction and discharge will be described below. [Suction stroke (-)] In the state shown in FIG. 27A, the working chamber Fu has the minimum volume, and corresponds to (B)-(D) and the rotary piston 3 corresponding to the top dead center of the suction side. With the rotation of the working chamber Fu, the working chamber Fu gradually increases, and the opened suction port In is opened.
The working fluid is sucked from. 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), near the bottom dead center in (A), the discharge hole Out opens and begins to compress the sucked fluid, and at the same time, the fluid starts to be discharged in the liquid, The discharge timing is timed by a discharge valve, a check valve, or the like attached to the discharge hole Out.
The discharge is continued to the vicinity of FIG.

As described above, the spherical rotary piston pump and the compressor of the present invention provide two comb-shaped operating chambers Fu, Fu in each half-moon shaped operating chamber Ha while the rotary piston 3 makes one rotation.
Has a characteristic that each rotation of the rotary piston 3 and the input shaft 2 has one discharge stroke for each rotation of the rotary piston 3 and the input shaft 2. The displacement 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] In addition, if the performance calculation of the spherical rotary piston pump and the compressor of the present invention is described in a fluid pump,
As with the conventional pump, the performance is the discharge rate Q [l / mi
n], and the discharge amount Q is represented by the following equation. Q = (ηυ · qp · N) / 1000 ηυ Volumetric efficiency of pump qp Displacement volume per rotation of 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, similarly to 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 obtained by multiplying the volumetric efficiency ηυ by the mechanical efficiency ηm.

[0075]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As described above, the spherical rotary piston pump and the compressor according to the present invention have a fluid pump, and It operates as a compressor. That is, in the present invention, one to four comb-shaped operating chambers (Fu or Fu, F
u, or Fu, Fu, Fu, or Fu, Fu, F
u, Fu), there are four comb-shaped working chambers Fu, Fu, Fu, Fu (spaces A, B, C, D) is formed, or the above-mentioned first to third embodiments
, Two comb-shaped operating chambers Fu, Fu (spaces A, D)
Or the spaces B, C) are formed, or two comb-shaped operation chambers Fu, Fu (spaces A,
The three forms of forming the space B or the spaces C and D) will be described in detail based on the following embodiments with reference to the drawings.

[0076]

Embodiment 1 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 configuration 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 solution is separated by two parallel cut planes straddling the S-circle surfaces aa and bb shown in FIG. 1 is divided into three parts, which are divided into a cylindrical or annular central portion on an S-circle surface and two side portions each composed of a crown smaller than a hemisphere. Is formed on the inner wall surface concentric with the S-plane larger than the spherical surface G as a skew plate housing 1b confined to the spherical surface G. Symmetrical concave inner walls 7a, 7a.

When the oblique plate housing 1b and the rotary piston housings 1a, 1a on both sides are united to form a spherical integrated structure, the two rotary piston housings 1a having the inner surface of the oblique plate housing 1b as the groove bottom. , 1a are formed between the circumferential edges of the concave inner walls 7a, 7a in the groove-shaped gap orbiting along the extension plane of the S-circle surface as the raceway gap 9. Then, the rotating piston housing 1a on the X-axis crosses the Y-axis of the center line of the raceway 9 at an angle θ at the spherical center O with the spherical axis O.
Main bearings 8 and 8 having bearing holes are provided through the opposing walls of 1a, and both main bearings 8 and 8 are fitted with both-side shaft necks of the input shaft 2 having a linear axis with the X axis as a rotation axis. To allow the bearing to rotate freely. The input shaft 2 is provided with a connection element (see FIGS. 9 and 10) formed of either a pin post of the pin joint joint 16 or a pin receiving hole which is located at the ball center O and has the M axis as a connection axis.
Is a pin receiving hole).

Further, the concave inner wall 7 of each rotating piston housing 1a forming a spherical surface G
and the arcuate surface 13 of the outer peripheral surface rotatably slidably in contact with a, and the front and back arcuate surfaces 14, 14 which form the arcuate contour plane of the arcuate surface 13.
And two of the bow-shaped plates formed by the bow-shaped chords of the front and back bow-shaped chords are symmetrically arranged with the respective chord sides facing each other with the K axis interposed therebetween, and face each other. A rotary piston 3 having a substantially circular plate is formed by interposing a columnar intermediate shaft 4 having a K-axis mounted on the chordal side surface of the two bow-shaped plates.

The rotary piston 3 penetrates from the two arcuate surfaces 13, 13 on the X axis along the R-circle included in the rotary piston 3 toward the center of the intermediate shaft 4, and the input shaft 2 is loosely inserted. A pin joint joint 1 corresponding to the shaft center 17 of the input shaft 2 with the M axis as a connection axis at a central portion of the piston through hole 15 in the intermediate shaft 4.
Six piston pivots 18 (pin posts in FIGS. 9 and 10) are provided. Then, the piston pivot 18 is pivotally attached to the central axis 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. Also, the intermediate shaft 4 of the rotating piston 3
At both ends, any one of the hinge pins 20 and 20 of the hinge joint 19 and the hinge pin receivers 21 and 21 (the hinge pin receivers in FIGS. 21 and 21).

The opening formed by the elliptical shape of the piston passage hole 15 has a minor axis slightly larger than the axis diameter of the input shaft 2, and a major axis corresponding to the rotational axis X, Y of the input shaft 2 and the swash plate 5. Intersection angle θ
The rotating piston 3 apparently reciprocates on the input shaft 2 as the rotating piston 3 rotates with its major axis being the amplitude length. Therefore, the rotating piston 3 rotates together 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 makes one reciprocation in the major axis direction of the piston through-hole 15 per one rotation. .

On the other hand, on the S-circular surface in the housing 1, symmetrically identical arcuate surfaces 22, which respectively correspond to the arcuate surfaces 14, 14 of the rotary piston 3, are provided on opposite sides of the intermediate shaft 4 of the rotary piston 3. And two bow-shaped plates formed on the chord side of the arcuate surfaces 22 and 22 and chord side surfaces 23 of which the geometrical condition is slidably contacted with the axial column surface of the intermediate shaft 4. An annular swash plate ring 24 rotatably slidably fitted in the raceway 9
Skew plate 5 formed into one circular plate by being joined inside
Is arranged. In other words, the skew plate 5 is formed of an arc-shaped subarc that is smaller than a semicircle on the same plane and an arc-shaped chord that passes both ends of the subarc, and symmetrically arranges the arcuate contour surfaces of the two arcuate plates outward. Orientation so that the chordal sides 23 face each other, and a skew plate ring 24 formed on the inner peripheral surface which engages with both arcuate contour surfaces is arranged outside the respective arcuate plates to join them. For example, the whole shape is formed in a circular plate.

The skew plate 5 has four sides facing the chord sides 23, 23 facing each other with the K axis interposed therebetween and the opposing surfaces of the skew plate ring 24 facing the K axis. A window-shaped gap portion penetrating in a rectangular shape on the K axis is formed, and the skew plate ring 2 located at the points Ka and Kb of the gap portion is formed.
On opposite sides of the rotary piston 4, connecting elements (hinge pins 20, 20 in FIGS. 9 and 10) corresponding to the hinge joint 19 elements mounted on both ends of the intermediate shaft 4 of the rotary piston 3 are provided. Then, if the intermediate shaft 4 of the rotary piston 3 is fitted into the window-shaped gap of the swash plate 5 along the axial column, the 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, and the chordal surfaces 23, 23 of the swash plate 5 and the shaft surface of the intermediate shaft 4 are sealed in sliding contact with each other. The opposite surfaces of the sloping plate ring 24 remaining as window frames are also hermetically sealed in sliding contact, and two circular plates of the rotating piston 3 and the swash plate 5 are used as the intermediate shaft 4.
The upper part is assembled so as to be able to slidably intersect in the ± θ angle range with the intersection line K as the axis of connection.

As a result, each semicircle of the rotary piston 3 assembled to the swash plate 5 is provided with the concave inner wall 7a of the rotary piston housing 1a, 1a provided by the semicircle.
The arcuate surfaces 13, 13 of the swash plate 5 are accommodated in the skewed plate housing 24 while the swashed plate rings 24 are held in an immovable manner. The input shaft 2 and the rotary piston 3 are assembled and connected to a pin joint joint 16 at the center of the inside of the rotary piston 3, and the rotary piston 3 and the swash plate 5 are hinged at both ends of the intermediate shaft 4. The joint 19 is constructed and connected.

Then, the oblique plate 5 on the S-circle surface closes the concave inner walls 7a, 7a of the rotary piston housings 1a, 1a, and the semi-lunar working chamber H of a constant volume space which forms a hemisphere 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 rotating piston 3 on the R-circle changes volume in inverse proportion. D. Further, a suction hole In and a discharge hole Out for a working fluid penetrating the wall of the housing 1 are provided facing the respective half-moon-shaped working chambers Ha.

When the rotation of the input shaft 2 is given in the direction of the arrow, the rotation of the input shaft 2 is transmitted to the pin joint joint 16 and the pair is connected as shown in FIGS. 25 and 26 (a) to (l). Cooperating rotation of the rotating piston 3 and the swash plate 5
Accordingly, the gap between the rotating piston 3 and the swash plate 5 changes, and the working chambers A, B, C, and D formed between the plate surfaces also increase or decrease in volume. When the volumes of the working chambers A, B, C, and D increase, the working fluid is sucked from the suction holes In provided by the respective working chambers, and when the volumes 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 configuration of the second embodiment and the common mode 1, and is similar to the configuration of the above-described first embodiment. The chambers A, B, C, and D are formed. In order to restrict the phase of the swash plate 5, the swash plate ring 24 and the swash plate ring 24
In this embodiment, the skew plate ring 24 is not attached to the skew plate 5 in contrast to the above-described first embodiment having the orbital gap 9 of the orbital groove in which the sloping plate fits. 5 has a track bearing 25 of a groove orbiting the outer peripheral surface of the housing 5, and a track ring 10 of a ring fitted to the track bearing 25 is fixed to the inner wall surface 7 of the housing 1 on the S-circle surface. The inner wall surface 7 is provided with a convex ring attachment to the concave groove of the raceway gap 9 in the first embodiment.

The main bearings 8, 8 at the points P, P are provided with the input shaft 2 having the shaft center 17 of the pin joint 16 at the spherical center O in the same manner as in the first embodiment. The input shaft 2 is inserted and the input shaft 2 is inserted to support the rotating piston 3. The rotary piston 3 on the R-circular surface which is pivotally supported by the input shaft 2 is a circular plate having the intermediate shaft 4 interposed between two symmetrically arranged arcuate plates. The skew plate 5 placed on the S-circle surface on the raceway ring 10 is also a circular plate in which the intermediate shaft 4 is interposed between two symmetrically arranged bow plates.

The four columns of the intermediate shaft in the second embodiment are as follows.
The shaft cylinder is cut into a plurality of rings (three in FIGS. 11 and 12) by a parallel plane on both bottoms, and a central portion thereof is fixed to the both bowed chord sides of the rotary piston 3 as a piston intermediate shaft 4a. Both end portions are fixed to the both bowed chord sides of the swash plate 5 as skew plate intermediate shafts 4b, 4b, and the piston intermediate shaft 4a and the skew plate intermediate shafts 4b, 4 of the round section joint portion.
a hinge pin and hinge pin receivers 20, 21, 20, 21 for providing the K-axis line to each other as a connection base axis at the center of the bottom surface
Are connected and fitted to form the hinge joint 19. Also,
As described above, the swash plate 5 includes the swash plate intermediate shafts 4b, 4b.
The orbital bearing 25 of a groove orbiting the outer peripheral surface including the bottom surface of the rotary centrifugal side is cut so that the orbital ring 10 is rotatably fitted.

As a result, 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 facing each other with the orbital ring 10 protruding inside as a boundary, and the concave inner walls 7a, 7a are inclined. The semi-circular working chambers Ha, Ha are formed in a constant volume space by the incorporation of the row plate 5, and the semicircular portions of the rotating piston 3 are accommodated in the respective concave inner walls 7a, 7a in a non-immediate manner. Each of the chambers Ha, Ha is formed into two sealed comb-shaped working chambers A, B, C, D each of which has a volume changed in inverse proportion. 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 swash plate 5 to rotate in cooperation with each other, as in the case of the first embodiment, and the respective working chambers A, B, C , D, the working fluid is sucked from a suction hole In formed at an appropriate position on the wall of the housing 1 when the volume increases, and a discharge hole formed similarly when the volume decreases. The working fluid is discharged from the Out.

[0090]

Embodiment 3 The orbital ring 10 fixed to the inner wall surface 7 of the housing 1 in the embodiment 2 can be constituted as a movable part in the housing 1. 13 and FIG. 1 based on the configuration of the common mode 1 with the third embodiment.
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. The controller CA sets the tilt angle of the swash plate 5 to 0.
The stroke of the rotary piston 3 is changed by continuously changing the angle to ± θ to vary the discharge flow rate.

That is, in this embodiment, a pattern-shaped orbital ring consisting of an outer peripheral surface rotatable in the direction of its own ring axis inside the inner wall surface 7 of the housing 1 and a round pillar fixed to both opposing outer peripheral surfaces on the diameter center line. A track ring 6 having a shaft 11 and a movable ring formed only in a direction perpendicular to both the X and Y axes is provided on both the X and Y axes, and the opposing wall of the housing 1 on the Z axis at the points e and e. Orbital ring bearings with the Z axis as the bearing axis
Is provided. Then, the track ring 6 is rotatably fitted to the track bearing 25 of the swash plate 5 orbiting groove and assembled, and the track ring shafts 11 are rotatably fitted to the track ring bearings 12. A control device CA (not shown) for attaching a connecting terminal to the shaft ring of the orbital ring shafts 11, 11 and freely changing the tilt angle of the swash plate 5 to the terminal of the shaft ring, though not shown. Are connected.

Then, the control device CA displaces the fixing stop position of the orbital ring shafts 11, 11 according to the pump discharge pressure, and the displacement of the fixing position changes via the orbital ring 6 to the tilt angle ( 0 ± θ) is automatically changed, but the change in the inclination of the swash plate 5 changes the sliding stroke of the rotary piston 3, and the stroke increases as the inclination increases and the stroke decreases as the inclination decreases. The necessary discharge amount corresponding to the discharge pressure is secured by changing the absolute volume amount, which is the displacement volume in one rotation of the shaft of each of the comb-shaped operation chambers A, B, C, and D.

[0093]

Fourth Embodiment In the structure of the first to third embodiments, the working chamber in the housing 1 is replaced by four working chambers Fu, Fu, Fu, Fu.
It is possible to operate with two working chambers Fu, Fu based on the configuration. This embodiment shown in FIG. 15 is based on the first embodiment and the common mode 2, and has two working chambers A, D in which the four working chambers A, B, C, and D are arranged in the axial direction in the configuration of the first embodiment. Or two working chambers B and C are replaced.

In this embodiment, as in the first embodiment,
In the above solution, the housing 1 in which the relations of points, lines and surfaces are set is divided into three by two parallel cut planes straddling the S-circle surfaces aa and bb shown in FIG. As the swash plate housing 1b, each of both sides is a rotary piston housing 1a, 1a, and when they are united on the same line, the inside of the swash plate housing 1b restrains the swash plate ring 24 in a rotatable manner. The input shaft 2 is formed in a groove-like gap 9 and has a shaft center 17 of the pin joint joint 16 element at the position of the spherical center O on the opposing walls of the rotary piston housings 1a, 1a on the X axis. The main bearings 8, 8 to be inserted and supported by the bearing are provided through.

On the other hand, in the difference from the first embodiment, in this embodiment, the circular rotating piston 3 is different from the first embodiment in that the spherical arc surface 13 of the outer peripheral surface of rotation and the two chords on the same plane sandwiching the K-axis line are provided. The substantially circular plate rotating piston 3 having a hemispherical shape as a whole is composed of the arcuate surfaces 14, 14 and the columnar intermediate shaft 4 merged in a semi-embedded manner between the two arcuate surfaces 14, 14. 1, the rotary piston 3 has a piston through hole 15 for allowing the input shaft 2 to be loosely inserted therein, a piston pivot 18 of the pin joint 16 located at the spherical center O, and hinge joints at both ends of the intermediate shaft 4. 19 connecting elements.

Further, in the difference from the first embodiment, the circular skew plate 5 formed by connecting the skew plate ring 24 to two symmetrically arranged bow plates is different from the skew plate of the fourth embodiment. The row plate 5 is a circular plate having a window-shaped gap in which one bow-shaped plate is fixed inside the swash plate ring 24 and penetrates more than a semicircle with the chord side surface 23 as a side. A connecting element corresponding to the hinge joint 19 element provided at each end of the intermediate shaft 4 is provided with a skew plate ring 24 located on the point Ka, point Kb side.
Are provided on the opposite sides of the skewed plate 5, the four columns of the intermediate shaft of the rotary piston 3 are fitted into the windows through which the swash plate 5 penetrates, and the hinge joint 19 is formed with both pieces. Are connected so that the ± θ angle range can be slidably set with the intersection line K as the connection axis.

Eventually, the swash plate 5 on the S-circle surface closes the biconcave inner walls 7a, 7a of the rotating piston housings 1a, 1a, and the semi-lunar operation of the constant volume space having a hemispherical shape on both sides of the skew plate 5. Chambers Ha, Ha are formed and the half-moon-shaped working chambers Ha, H are formed.
a is formed in each of comb-shaped working chambers A and D or B and C in which the rotating piston 3 on the R-circle makes a volume change in inverse proportion on the same plane, and each of the working chambers A and D is formed. At an appropriate position on the wall of the housing 1 facing the half-moon-shaped working chamber Ha, a suction port In and a discharge port Out of a working fluid are provided. Since the rotating piston 3 and the skew plate 5 which are transmitted to the pin joint joint 16 and cooperate with each other to rotate cooperatively and increase or decrease the volume of the working chambers A and D or B and C in the operation thereof, the volume increases. In this case, the working fluid is sucked from the suction hole In, and when the working fluid is reduced, the working fluid is discharged from the discharge hole Out.

[0098]

[Embodiment 5] This embodiment shown in FIG.
In the same manner as in the configuration of the first embodiment, two comb-shaped working chambers A and D or B and C are arranged in the housing 1 in the axial direction, and are based on the configurations of the second embodiment and the common mode 2. is there. In order to restrain the phase of the swash plate 5, the orbital gap 9 of the circumferential groove provided on the inner wall of the housing 1 in the above-described fourth embodiment is disposed around the outer circumferential surface of the swash plate 5 in the same manner as in the configuration of the second embodiment. The orbital ring 10 of the ring fitted to the orbital bearing 25 provided in the groove is fixed to the inner wall surface 7 of the housing 1 on the S-shaped surface in a protruding manner. The input shaft 2 having sixteen shaft center points 17 is inserted into and supported by the main bearings 8, 8 at points P, P.

On the other hand, the rotating piston 3 has two arcuate surfaces 1, 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 intermediate shaft 4 between the two arcuate surfaces 14, 14.
The oblique plate 5 is a substantially semi-circular plate in which at least both side portions of the intermediate shaft 4 are attached to one bow-shaped plate, As shown in FIG. 16, the intermediate shaft 4 is a circular plate having an arcuate plate on which both sides of the intermediate shaft 4 are attached, and the opposite side of the arcuate plate is also connected in an arch shape to have a circular outer peripheral surface as a whole. The four pillars are fixed to the rotary piston 3 at the central part of the three divisions as the piston intermediate shaft 4a, and the both sides are fixed to the swash plate 5 as the swash plate intermediate shafts 4b, 4b, as in the above-described Embodiments 2 and 3. A hinge pin receiver 2 fitted to the hinge pin
The hinge joints 19 of 0, 21, 20, 21 are formed and connected.

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

[0101]

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

That is, similarly to the configuration of the third embodiment, the orbital ring shafts 11, 11 of the orbital ring 6 are supported by the orbital ring bearings 12, 12 provided on the wall of the housing 1 on the points e and e, and When a control device CA for controlling the inclination of the skewing plate 5 is attached to the orbital ring shafts 11 and 11 so that they are linked with each other, the control device CA causes the inclination angle (0 to ±±) of the skewing 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 of each of the working chambers A, D or B, C in one rotation of the shaft to secure a discharge amount corresponding to the discharge pressure. I do.

[0103]

[Embodiment 7] In this embodiment shown in FIGS. 18 and 19, two working chambers A and B or two working chambers C are arranged in the direction perpendicular to the axis based on the structure of the first embodiment and the common mode 3. , D. That is, in this embodiment, in the above-mentioned solving means, the interior of the housing 1 in which the relations of points, lines and surfaces are set is defined by one cut plane parallel to the S-circle aa shown in FIG. A skew plate housing 1b formed in a large concave space, and a hemispherical rotary piston housing 1a in which a concave inner wall 7a forming a spherical surface G faces a concave inner wall of the skew plate housing 1b. The rotary piston 3 is formed into a substantially semi-circular plate in which an arcuate plate and an intermediate shaft 4 are combined in a housing 1 configured as follows.
The swash plate 5 also has one of the two plate surfaces as a surface on which the working chambers Fu and Fu are formed, and the working chambers Fu and the surface on which the Fu is formed face the plate surface of the rotary piston 3 so as to be interlocked with each other.

Therefore, the concave space portion of the swash plate housing 1b is formed on the inner peripheral surface concentric with the Y axis as the raceway space 9 for rotatably restraining the swash plate 5 in this embodiment. Also, the main bearings 8 and 8 are provided through the wall of the rotating piston housing 1a and the side wall of the oblique plate housing 1b facing each other on the X axis, and the pin joint joint 16 is located at the spherical center O position in the main bearings 8 and 8. The input shaft 2 having the shaft center 17 is supported. On the other hand, the semicircular plate-shaped rotary piston 3 is provided with a connecting element of the hinge joint 19 on both sides of the intermediate shaft 4 at the points Ka and Kb, similarly to the configuration in any of the above-described embodiments. 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 spherical center O position in the piston through hole 15 so as to be provided at the shaft center 17 of the input shaft 2. Pivot.

The skew plate 5 has two bow-shaped surfaces 22, 22 with the chords facing each other on the same plate surface, and the two bow-shaped surfaces 2, 22.
A chord side surface 23 of a semi-cylindrical concave surface formed in a groove-like concave portion which slidably contacts the intermediate shaft 4 pillars between the chord sides of 2, 2;
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 rotating surface is larger than the circular plate diameter, and is annularly fitted into the raceway gap 9 so as to be able to rotate and slide. The skewed plate ring 24 is formed with a circular plate. The skewed plate through-hole 26 for inserting the input shaft 2 is opened from the center of the chordal side surface 23 to the outer sliding contact surface 27, and the piston through-hole 15 is formed. Intermediate shaft 2
The hinge joints 1 at both ends of the intermediate shaft 4 are provided on both sides of the oblique plate ring 24 on the side of the points Ka and Kb while being joined to the opening.
Connection elements corresponding to the nine elements are provided. Then, four intermediate shafts are inserted into the chord side surfaces 23 of the swash plate 5,
The swash plate 5 and the rotating piston 3 are connected by a hinge joint 19 to ±
When the θ angle range is connected so as to be able to slide, the rotating piston 3
Is accommodated in the concave inner wall 7a of the rotary piston housing 1a while the arcuate surface 13 is kept in an immovable state, and the skew plate ring 24 of the skew plate 5 is also freely rotatable in the raceway 9 of the skew plate housing 1b. It is stored in a proper fitting state.

In this embodiment, the oblique plate 5 on the S-circle surface closes the concave inner wall 7a of the rotary piston housing 1a to form a semi-lunar working chamber Ha of a constant volume space having a hemispherical shape. The half-moon-shaped working chamber Ha is formed as two comb-shaped working chambers A and B or C and D in which the volume of the rotating piston 3 on the R circular surface changes in inverse proportion. In addition, a suction port In and a discharge port Out of the working fluid are provided at appropriate positions of the housing 1 facing the half-moon working chamber Ha. Then, the rotation in the direction of the arrow given to the input shaft 2 causes the rotary piston 3 and the swash plate 5 to cooperately rotate via the pin joint joint 16 and, accordingly, the working chambers A and B or C and D. The working fluid is sucked from the suction hole In when the volume increases, and the working fluid is discharged from the discharge hole Out when the volume increases.

[0107]

Embodiment 8 In this embodiment, a fixed shaft is attached to the swash plate 5 in place of the swash plate through-hole 26 penetrating the center of the swash plate 5 in the structure of the above-described embodiment 7, and the operation is performed. . That is, as shown in FIG. 20, the input shaft 2 is configured as shown in FIG. The input shaft 2 is configured such that a shaft column is attached to only one side of the shaft center pivot 17 and is supported by a main bearing 8 provided on the wall of the rotating piston housing 1a. The shaft hole 26 is not formed. On the contrary, a handle-shaped round bar is fixedly fixed to the center of the outer sliding contact surface 27 as a skew plate shaft 28, and the skew plate housing 1b is formed on the skew plate shaft 28. A swash plate bearing 29 is provided at the center of the wall to cope with this.

In this case, the mutually extending straight lines of the input shaft 2 and the swash plate shaft 28 are made to coincide with the X and Y axes intersecting at an angle θ on the spherical center O of the concave inner wall 7a of the housing 1. However, a bearing is provided in each of the walls of the housing 1 on the X and Y axes which are opposite to each other, and one of the walls of the input shaft 2 is formed as a main bearing 8 which penetrates the wall of the rotating piston housing 1a on the X axis. The skewed plate shaft 28 is inserted through the skewed plate shaft 28 as a skewed plate bearing 29 that bores the wall of the skewed plate housing 1b on the Y axis. In other words, also in this embodiment, the input shaft 2 and the swash plate 5 rotate on a stereoscopic rotation axis separated by an angle θ, and the input shaft 2 and the swash plate 5 The rotating piston 3 (the rotation axis L) whose direction is restrained and supported makes a conical movement along the conical locus U.

[0109]

[Embodiment 9] This embodiment shown in FIG.
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 mode 3. This embodiment is different from the seventh embodiment in that:
The same ring as the race ring 10 attached in the second and fifth embodiments is fixed to the inner wall surface 7 of the housing 1 on the S-circle with respect to the raceway 9 of the concave space of the housing 1 that restrains the phase of the swash plate 5. .

In this case, the rotary piston 3 is a semicircular plate in which at least a central portion of the intermediate shaft 4 whose column is arcuate and is cylindrical is fixed to an integral structure, and the inclined plate 5 is the same as the skew plate 5. A circular plate formed by the two arcuate surfaces 22, 22 on the plate surface and the outer sliding contact surface 27 on the back surface of the two arcuate surfaces 22, 22, including the rotation outer peripheral surface, forms an intermediate shaft between the two arcuate surfaces 22, 22. 4 is a circular plate to which at least both side parts are fixed, so that the four intermediate shafts are divided into at least three parts as in the case of the second and fifth embodiments, and the central part is a rotating piston as a piston intermediate shaft 4a. 3 and both sides are swash plate intermediate shafts 4
b, 4b, which are fixed to the swash plate 5 and the joint portions thereof are provided with hinge pins and hinge pin receivers 20, 21,
The swash plate 5 comprising the hinge joints 20 and 21 formed and connected, and including the circumscribed bottom surfaces of the two skew plate intermediate shafts 4b and 4b.
The orbital ring 10 is rotatably fitted to the orbital bearing 25 in a groove provided on the outer peripheral surface of the orbital.

As a result, a semi-lunar working chamber Ha is formed in the housing 1 by incorporating the skewing plate 5, and the two comb-shaped working chambers A, in which the rotating piston 3 changes the volume of the half-moon working chamber Ha in inverse proportion. B, or C and D, and a suction hole In and a discharge hole Out are formed at appropriate positions on the wall of the housing 1. Are rotated cooperatively to increase or decrease the volume of the working chambers A and B or C and D. When the volume increases, the working fluid is sucked from the suction hole In, and when the volume decreases, the working fluid flows from the discharge hole Out. The working fluid is discharged.

[0112]

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

That is, the tenth embodiment shown in FIG.
In the same manner as in the configurations of the third and sixth embodiments, the movable race ring 6 is mounted within the inner wall surface 7 of the housing 1 which is fitted to the race bearing 25 of the swash plate 5 and supports the swash plate 5. The bearing ring shafts 11, 11 attached to both sides opposite to each other are fitted and fitted with bearing ring bearings 12, 12 provided on the wall of the housing 1 on the point e, e side, and are attached to the bearing ring shafts 11, 11. Swash plate 5
A control device CA for controlling the inclination of the camera is attached and linked. That is, the control device CA automatically changes the tilt angle (0 to ± θ) of the swash plate 5 in accordance with the discharge pressure of the pump, so that each of the working chambers A and B or the axis 1 of C and D By changing the displacement in rotation, a discharge amount corresponding to the discharge pressure is ensured.

[0114]

Embodiment 11 This embodiment shown in FIG. 23 is based on the configuration of the fourth embodiment and the common mode 3, and is based on the configuration of the eighth embodiment.
Working chambers A and B arranged in the direction perpendicular to the axis as in the configuration of
Alternatively, the skewed plate housing 1b is formed in a raceway space 9 having a concave space larger than the diameter of the S-circle surface. The peripheral wall surface corresponding to the housing 1b is also formed into a spherical surface G, and the skew plate 5 is formed and incorporated in the peripheral wall surface.

That is, in this embodiment, the main bearing 8 on the X-axis is attached to the housing 1
And a skew plate bearing 29 on the Y-axis located on the opposite side thereof penetrates, and the input shaft 2 is fixed to the shaft center pivot 17 in the same manner as in the above-described eighth embodiment, and only one side of the shaft column is fixed. Are fitted in the main bearing 8 with the shaft and neck inserted therein, and the rotary piston 3 is fixed to the arc-shaped plate at least in the middle of the intermediate shaft 4 divided into at least three parts in the same manner as in the above-described embodiments 9 and 10. It is a semicircular plate.

The skewed plate 5 has two arcuate surfaces 2 on the same plate surface.
2 and 22 and both arcuate surfaces 2 sliding on the inner wall surface 7 of the spherical surface G
The outer sliding contact surface 27 of the outer peripheral surface including the back surfaces of the intermediate shaft 4 is fixed between the two arcuate surfaces 22, 22 at least into three parts, and the center of the outer sliding contact surface 27. The skewed plate bearing 29 is inserted into the skewed plate bearing 29, and a pattern-shaped swashed plate shaft 28 for projecting the skewed plate 5 main body to the rotation of the stereotactic shaft is protruded. Also in this embodiment, when rotation in the direction of the arrow is given, the volume of the working chambers A, B or C, D increases or decreases, and when the volume increases, the working fluid is sucked from the suction hole In, and the volume decreases. In this case, the working fluid is discharged from the discharge hole Out.

[0117]

Embodiment 12 In the embodiment shown in FIG. 24, the portion of the swash plate bearing 29 which is formed at the fixed position of the housing 1 in the above-mentioned Embodiment 11 is movable only on a plane passing through both the X and Y axes. The phase of the swash plate shaft 28 is changed so that the tilt angle (0 to ± θ) of the swash plate 5 can be arbitrarily changed.

That is, the wall of the housing 1 through which the swash plate shaft 28 penetrates on a plane passing through both the X and Y axes is opened at least within a range of ± θ angle with respect to the X axis, and the skew plate shaft is provided at the open portion. At the same time, a swash plate bearing 29 into which the swash plate 28 is inserted is attached, and although not shown, the control device CA for controlling the movement of the skew plate bearing 29 in the ± θ angle range with respect to the X axis is set to a point e on the Z axis. , And e are attached to the fulcrum and linked. Eventually, the control device CA automatically changes the tilt angle (0 to ± θ) of the swash plate 5 according to the pump discharge pressure, and the operating chambers A,
By changing the displacement volume in one rotation of the shaft B or C and D, a discharge amount corresponding to the discharge pressure is always ensured.

[0119]

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

[0120]

The reciprocating piston pump and the reciprocating piston compressor, which are used at high pressure and high speed rotation among the conventional fluid pumps and compressors, and are most versatile, have a cylindrical cylinder and a piston as their basic structures. And the basic structure and operation have many problems as described above.

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

On the other hand, the spherical rotary piston pump and compressor of the present invention have a completely different shape from the conventional piston pump and compressor including gears, vanes, etc., and have a spherical or spherical basic structure. . This spherical and spherical structure is basically strong and robust against impact load and thermal stress, and the structure of a combination of a spherical body and two circular pistons (the rotating piston 3 and the oblique plate 5) housed in the spherical body is as follows. When the pressure becomes high, the leakage from the discharge side inside the pump to the suction side on the low pressure side or into the housing is small, that is, the working space Fu space with extremely high volumetric efficiency and high sealing performance is formed and maintained. Is 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 skew plate 5 is also rotated by the hinge joint 19. . Then, the rotating piston 3
And the swash plate 5 are expanded to expand the working chamber Fu space closed by the two arcuate surfaces 14 and 22 of the rotating piston 3 including the inner wall surface 7 of the housing 1 and the intermediate shaft 4 and the skew plate 5. Then, the expanded working chamber Fu space forms a vacuum state and sucks the working fluid. With the rotation, the arcuate surface 14 of the rotary piston 3 is rotated by one rotation of the
Is performed, and the suction and discharge are continuously performed into the working chamber Fu space by repeating the slide.

As described above, in the spherical rotary piston pump and compressor according to the present invention, the rotational force applied to the input shaft 2 directly expands the space between the rotary piston 3 and the swash plate 5 to perform a pumping action. Has structural features. Therefore, there are no factors that cause various problems such as inertial force due to linear reciprocation of the piston such as conventional reciprocating piston pumps and reciprocating compressors. It is made up of the space and simple parts, so that there is no waste of space and complexity, and it is extremely small and lightweight compared to other pumps and compressors having the same displacement volume. Moreover,
There is no element of friction wear, particularly uneven wear components such as reciprocating piston pumps and compressors, and it is not always necessary to install suction and discharge valves. It should be noted that if pressure oil is supplied to the suction side as a hydraulic pump, it can be used as a hydraulic motor for an actuator that acts in the opposite direction of the hydraulic pump.

[0125] The total efficiency (pump efficiency) represented by the product of the volumetric efficiency and the mechanical efficiency is generally the highest in a conventional pump in a piston pump, but is basically an aggregate of circles. Certain fluid pumps and compressors of the present invention have a large sliding efficiency, which is very advantageous for sealing because the sliding contact surface is circular as described above, and shows a high volumetric efficiency in which the ratio of the actual discharge amount that decreases as the pressure increases increases. In addition, the rotating piston without jerking has excellent mechanical efficiency indicating the ratio of the effective shaft input, and exhibits high pump efficiency. Alternatively, even when the speed is changed by a DC motor or an engine (internal combustion engine), the self-priming ability at low and high speed ranges is excellent, and almost no noise and vibration are generated. It is possible, and the rotation speed at which continuous operation is possible is high, and the rated pressure and the rated rotation speed are high.

As described above, since the spherical rotary piston pump and compressor of the present invention have a spherical structure, they are rich in rigidity, durability, simple and straightforward mechanism, small and lightweight, inexpensive, and have a low discharge pressure. Even if it changes, there is little change in the discharge amount, and the pulsation of the discharge amount can be reduced by increasing the number of working chambers Fu. High-performance fluid pump that has high mechanical efficiency and volumetric efficiency and can withstand high pressure and high speed use , Compressor.

[Brief description of the drawings]

FIG. 1 is a partially longitudinal perspective view of a basic graphic showing the principle of the present invention.

FIG. 2 is a perspective view showing a change in angle of a basic graphic.

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

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

FIG. 5 is a perspective view showing a change in the angle of a basic graphic.

FIG. 6 is a perspective view showing a change in angle of a basic graphic.

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

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

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

FIG. 10 is an exploded perspective view, partly in section, of FIG. 9;

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

FIG. 12 is an exploded perspective view, partly in section, of FIG. 11;

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

FIG. 14 is an exploded perspective view, partly in section, of FIG. 13;

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.

FIG. 19 is an exploded perspective view of a part of FIG. 18;

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

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

FIG. 22 is a side view showing a tenth embodiment of the present invention.

FIG. 23 is a side view showing Embodiment 11 of the present invention.

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

FIGS. 25A, 25B, 25C, 25D, and 25F are partial longitudinal side views each showing (a), (b), (c), (d), (e), and (f) showing an operation and a change in volume of a working chamber space in the present invention.

26 (g), (h), (i), (j), (k) showing the operation in the present invention and the change in the volume of the working chamber space, following FIG.
FIG.

FIG. 27 is a schematic front view showing the operation progress of the suction and discharge strokes according to the present invention.

[Explanation of symbols]

G sphere O sphere center of sphere G r radius of sphere G X X-axis (axis of attachment of input shaft) Y Y-axis (axis of formation of S-circle, rotation axis of oblique plate) θ θ angle (X-axis and Y-axis P (Point where the X axis intersects the spherical surface G) Q Q Point (Point where the Y axis intersects the spherical surface G) U Conical locus U (Points P and Q are the diameter bottom surface, spherical center O M M axis (vertical axis of X axis, coupling axis of pin joint joint) Z Z axis (straight line orthogonal to both X and Y axes, raceway bearing forming axis) e e point (Z R R circular surface (horizontal circular surface on X-axis) S S circular surface (vertical circular surface on Y-axis) L L-axis (rotational axis of R-circle) K K-axis (R Ka One end point at both ends of the K axis Kb The other end point at both ends of the K axis Ha Ha Semilunar space, semilunar work Room Fu Comb-shaped space, comb-shaped working chamber In Suction hole, suction hole Out Outlet hole, discharge hole CA Control device for changing the inclination of the swash plate A space A, comb-shaped working room A B space B, comb-shaped working room BC space C, comb-shaped operating chamber CD space D, comb-shaped operating chamber D 1 housing 1a rotating piston housing 1b swash plate housing 2 input shaft 3 rotating piston 4 intermediate shaft 4a piston intermediate shaft 4b swash plate intermediate shaft 5 Swash plate 6 Orbital ring 7 Inner wall surface, spherical inner wall 7a Concave inner wall of rotary piston housing 8 Main bearing 9 Orbital gap of housing 10 Orbital ring of housing 11 Orbital ring shaft 12 Orbital ring bearing 13 Spherical arc surface of rotary piston 14 Rotary piston Arcuate surface 15 Piston through hole 16 Pin joint joint 17 Center pivot 18 Piston pivot 19 Hinge joint 20 Hinge pin 21 Hinge pin receiver 22 Bow surface of swash plate 23 Chordal side surface of swash plate 24 Skew plate ring 25 Track bearing 26 Skew plate shaft hole 27 Sliding plate outer sliding contact surface 28 Skew plate shaft 29 Skew plate bearing

Claims (4)

[Claims] 1. A housing (1) having a spherical surface on an inner wall surface.
In the above, 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) to rotate the shaft and neck of the input shaft (2) having a straight axis. A raceway groove (9) on the inner wall surface of the housing (1) on the vertical plane of an axis which is freely inserted and whose axis (2) intersects with the input shaft (2) at an angle (θ) at an angle (θ). In the housing (1), at least an angle (θ × 2) in the horizontal direction on the input shaft (2) with a straight line orthogonal to the input shaft (2) at the spherical center (O) as a connection axis in the housing (1). The spherical arc surface (1) swinging in the range of
3), and a cylindrical intermediate shaft (4) is united with the chord side having a spherical arc surface (13) having an arcuate arc, and an arcuate surface (1) is formed on the plate surface.
4) A substantially plate-shaped rotating piston (3) having an input shaft (2)
Pivotally connected to the portion of the spherical center (O) of the above, and in the upper housing (1), hingedly intersect with the rotary piston (3) on the intermediate shaft (4), and the outer periphery of the edge is formed in a ring shape. The skew plate ring (24) is the raceway gap (9)
And a pin and a pin receiving hole are provided to each of both bottom surfaces of the intermediate shaft (4) and opposing opposite side portions of the oblique plate ring (24) in contact with the both bottom surfaces. A skew plate (5) of a circular plate having a connection element and being slidably connected to each other at least in an angle (θ × 2) range and having an arcuate surface (22) on a plate surface; (5) Closes the spherical inner wall (7) of the housing (1) to form a hemispherical working chamber (Ha) of a hemispherical space, and the rotating piston (3) combs the half-moon working chamber (Ha). It is formed in the comb-shaped working chamber (Fu) of the shape space, and is further exposed to the comb-shaped working chamber (Fu) so that the suction hole (I
and n) and a discharge hole (Out) as required. 2. A housing (1) having a spherical surface on an inner wall surface.
In the above, 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) to rotate the shaft and neck of the input shaft (2) having a straight axis. The housing (1) has an inner wall surface (7) on a vertical plane of an axis intersecting at an angle (θ) with its input shaft (2) at a spherical center (O) with a free axis. And a ring (10) protruding from the input shaft (2) is provided in the housing (1) at least in a horizontal direction on the input shaft (2) with a straight line orthogonal to the input shaft (2) at the spherical center (O) as a connection axis. A spherical arc surface (1) swinging in a range of an angle (θ × 2) and slidingly contacting the outer peripheral surface with the spherical inner wall (7)
A substantially plate-shaped rotary piston (3) formed in 3) and having an arcuate surface (14) on the plate surface is pivotally connected to the portion of the spherical center (O) of the input shaft (2), and the housing (1) Inside the rotating piston (3)
And a track bearing (25) of a groove intersecting in a hinge shape and circling around an arcuate surface (22) and an outer peripheral surface thereof.
A swash plate (5) of a circular plate into which the race ring (10) is rotatably fitted is provided at a crossing portion of the swash plate (5) and the rotating piston (3). 4) is divided by cut surfaces parallel to both bottom surfaces, and each of them is divided into a swash plate (5) and a rotating piston (3).
And a connecting element for providing a pin and a pin receiving hole to each other at each of the divided joining surfaces thereof so as to be able to slide at least in an angle (θ × 2) range. A plate (5) closes the spherical inner wall (7) of the housing (1) to form a hemispherical working chamber (Ha) of a hemispherical space, and the rotating piston (3) divides the semi-lunar working chamber (Ha). It is formed in the comb-shaped working chamber (Fu) of the comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
and n) and a discharge hole (Out) as required. 3. A housing (1) having a spherical surface on an inner wall surface.
In the above, 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) to rotate the shaft and neck of the input shaft (2) having a straight axis. The spherical center (O) is inserted into both the axis which is freely inserted and intersects with the input axis (2) at an angle (θ) at the spherical center (O) and the axis of the input axis (2).
The housing (1) has a circular hole in a raceway ring bearing (12) on both opposing walls, and the raceway ring bearing (12) is rotatable 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 the race ring (6) composed of a ring body provided on the shaft is freely rotatably supported, and the input shaft (2) is provided in the housing (1). The input shaft (2) is swung horizontally on the input shaft (2) at least in the range of an angle (θ × 2) with a straight line orthogonal to the spherical center (O) as a connection axis, and the outer peripheral surface is in sliding contact with the spherical inner wall (7). Spherical surface (1
A substantially plate-shaped rotary piston (3) formed in 3) and having an arcuate surface (14) on the plate surface is pivotally connected to the portion of the spherical center (O) of the input shaft (2), and the housing (1) Inside the rotating piston (3)
And a track bearing (25) of a groove intersecting in a hinge shape and circling around an arcuate surface (22) and an outer peripheral surface thereof.
A skew plate (5) of a circular plate into which the race ring (6) is rotatably fitted, and a cylindrical intermediate shaft (5) is provided at the intersection of the skew plate (5) and the rotary piston (3). 4) is divided by cut surfaces parallel to both bottom surfaces, and each of them is divided into a swash plate (5) and a rotating piston (3).
A pin and a pin receiving hole are provided on each of the divided joint surfaces so that the pins and the pin receiving holes are provided to each other so as to be slidable at least in an angle (θ × 2) range; The ring (6) is provided with a control device (CA) for selecting a tilt angle of the orbital ring (6) from the angle 0 to an angle ± θ with respect to the input shaft (2). 11), the swash plate (5) closes the spherical inner wall (7) of the housing (1) to form a hemispherical working chamber (Ha) of a hemispherical space, and the half moon 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 further exposed to the comb-shaped working chamber (Fu).
and n) and a discharge hole (Out) as required. 4. A housing (1) having a spherical surface on an inner wall surface.
In the above, 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) to rotate the shaft and neck of the input shaft (2) having a straight axis. The skew plate bearing (2) is also fitted on the wall of the housing (1) on a straight line which is freely inserted and intersects with the input shaft (2) at an angle (θ) at a spherical center (O).
The circular hole of 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) swinging upward at least in the range of an angle (θ × 2) and slidingly contacting the outer peripheral surface with the spherical inner wall (7).
A semicircular plate rotating piston (3) formed in 3) and having an arcuate surface (14) on the plate surface is pivotally connected to the portion of the spherical center (O) of the input shaft (2), and the housing (1) ) Contains the rotating piston (3)
And an outer peripheral surface which intersects with the inner wall surface (7) of the housing (1) so as to slidably contact the inner wall surface (7) and an arcuate surface (22) on the plate surface, and the oblique movement is provided at the center of the back surface side of the arcuate surface (22). Plate bearing (2
9) is provided a circular swash plate (5) having a handle-shaped swash plate shaft (28) into which the swash plate (5) and the rotating piston (3) are rotatably fitted. At the intersection, a cylindrical intermediate shaft (4) is divided by a cut surface parallel to both bottom surfaces, and each is divided into a swash plate (5) and a rotating piston (3).
And a connecting element for providing a pin and a pin receiving hole to each other at each of the divided joining surfaces thereof so as to be able to slide at least in an angle (θ × 2) range. A plate (5) closes the spherical inner wall (7) of the housing (1) to form a hemispherical working chamber (Ha) of a hemispherical space, and the rotating piston (3) divides the semi-lunar working chamber (Ha). It is formed in the comb-shaped working chamber (Fu) of the comb-shaped space, and is further exposed to the comb-shaped working chamber (Fu).
and n) and a discharge hole (Out) as required.