JPH1137065A - Displacement type fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce fluid loss of suction gas by communicating a compressor suction port to a plurality of spaces through communicating holes provided on an end plate and suction flow passages provided in a cylinder. SOLUTION: Working gas entering a closed vessel 3 through a suction pipe 13, enters the suction port 13a in a suction cover 10 fitted to a main bearing member 7, enters a displacement type compression element 1 through suction communicating holes 7a, and hereat a displacer 5 performs turning motion by rotation of a rotary shaft 6, the gas is compressed by reducing the volume of a compression operating chamber. The compressed working gas passes through discharge ports 8a formed on the end plate 8b of a sub-bearing member 8, pushes up discharge valves 9 to enter a discharge chamber 8c, and is carried away outward through a discharge pipe 14. In this case, three compression operating chambers are formed, they discharge gas in the phases shifted by 120 degrees, hence the fluid can be compressed smoothly and continuously, and fluid loss in the discharge process can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump, a compressor, an expander, and the like, and more particularly, to a positive displacement fluid machine.

[0002]

2. Description of the Related Art A reciprocating type fluid machine which moves a working fluid by repeating a reciprocating motion of a piston in a cylindrical cylinder has been used as a positive displacement type fluid machine, and a cylindrical piston has been eccentric in a cylindrical cylinder. A rotary (rolling piston type) fluid machine that moves a working fluid by rotating, meshing a pair of fixed scroll and orbiting scroll having an upright spiral wrap on an end plate, and orbiting the orbiting scroll. 2. Description of the Related Art A scroll type fluid machine that moves a working fluid by a hydraulic fluid is known.

A reciprocating fluid machine has the advantage that it is easy to manufacture and inexpensive because of its simple structure, but the stroke from the end of suction to the end of discharge is as short as 180 degrees in terms of the rotation angle of the rotating shaft. The problem is that the flow velocity in the discharge process is high, the performance is reduced due to the increase in pressure loss, and the reciprocating motion of the piston makes it impossible to completely balance the unbalanced inertial force of the rotating shaft system. There is a problem that is large.

[0004] In the rotary type fluid machine, although the stroke from the end of suction to the end of discharge is 360 degrees of the rotation angle of the rotating shaft, the problem that the pressure loss in the discharge process increases is smaller than that of the reciprocating type fluid machine. Since the gas is discharged once per rotation of the shaft, the fluctuation of the gas compression torque is relatively large, and there is a problem of vibration and noise as in the reciprocating fluid machine.

Further, in the scroll type fluid machine, the stroke from the end of the suction to the end of the discharge is as long as 360 ° or more in terms of the rotation angle of the rotating shaft (normally about 900 ° for air-conditioning applications). This has the advantage that the pressure loss of the gas is small, and generally a plurality of compression working chambers are formed, so that the fluctuation of the gas compression torque during one rotation is small and the vibration and noise are small. However, it is necessary to manage the clearance between the spiral wrap in the lap meshing state and the clearance between the end plate and the tip of the lap, so that high-precision processing must be performed and the processing cost is high. There is. In addition, there is a problem that the stroke from the end of suction to the end of discharge is as long as 360 degrees or more in terms of the rotation angle of the rotating shaft, and the longer the period of the compression process, the more internal leakage increases.

By the way, the displacer for moving the working fluid does not rotate relative to the cylinder into which the working fluid has been sucked, but revolves around a substantially constant radius, that is, makes a revolving motion to convey the working fluid. Japanese Patent Application Laid-Open No. 55-23353 (Reference 1), U.S. Pat.
02869 (Document 3) and JP-A-6-28075
No. 8 (Reference 4). The displacement type fluid machine proposed here comprises a piston having a petal shape in which a plurality of members (vanes) extend radially from the center, and a cylinder having a hollow portion substantially similar to the piston, This piston moves the working fluid by revolving in the cylinder.

[0007]

The displacement type fluid machine disclosed in the above-mentioned document 4 does not have a reciprocating portion unlike the reciprocating type, so that the imbalance of the rotating shaft system can be balanced. For this reason, there is a feature that vibration is small and a frictional loss can be relatively reduced because a relative sliding speed between the piston and the cylinder is small. However, the suction passage serves as both a large space formed in the casing and a wide space formed between the casing and the outer runner, and furthermore, the passage is temporarily restricted by the disk portion of the inner runner. Therefore, there has been a problem that the suction gas is overheated before flowing into the compression chamber from the compressor suction port, or a suction pressure loss due to the flow of the suction gas occurs, thereby deteriorating the compressor performance.

Further, in the above document 4, sufficient consideration is not given not only to the existence of the lubricating oil but also to the lubricating oil path and the like, and the means for supplying the lubricating oil into the compression working chamber is not specified. There were problems in terms of lubrication in the working chamber and ensuring sealing performance. Further, the stroke from the end of suction to the end of discharge of each compression working chamber formed by the plurality of vanes and cylinders constituting the piston is as short as about 180 degrees (210 degrees) at the rotation angle θc of the rotating shaft (rotary). (Approximately half of the formula is about the same as the reciprocating formula), so that there is a problem that the flow velocity of the fluid in the discharge process increases, the pressure loss increases, and the performance decreases. In the fluid machines disclosed in these documents, the rotation angle of the rotating shaft from the end of suction to the end of discharge of each compression working chamber is small, and the next (compression) stroke starts after the discharge of the working fluid ends. There is a time lag (time lag) until (end of inhalation),
Since the compression working chamber from the end of suction to the end of discharge is formed to be biased around the rotation axis, the mechanical balance is poor, and the piston as a reaction force from the compressed working fluid,
There is a disadvantage in that the rotation moment for rotating the piston itself excessively acts, and reliability problems such as friction and wear of the vane are likely to occur.

A first object of the present invention is to provide a swiveling swing type positive displacement fluid machine capable of reducing fluid loss of suction gas. A second object of the present invention is to solve the problems of friction and wear by maintaining good lubrication in the suction compression working chamber of the compression working chamber and enhancing the lubricating oil sealing effect to overcome the rotational moment acting on the displacer. It is an object of the present invention to provide a positive displacement type fluid machine with high reliability and high efficiency.

[0010]

A first object of the present invention is to dispose a displacer and a cylinder between end plates, and when the center of the cylinder and the center of the displacer are aligned, one is formed by the inner wall surface of the cylinder and the outer wall surface of the displacer. In a positive displacement fluid machine in which two spaces are formed and a plurality of spaces are formed when the positional relationship between the displacer and the cylinder is at a swiveling position, a compressor suction port and the plurality of spaces are provided on an end plate. By forming a communication state through a communication hole and a suction flow path provided in the cylinder, or disposing a displacer and a cylinder separately between end plates, and disposing a rotation shaft at a center portion of the displacer. A compression mechanism unit integrally constituted by a fastening means such as a bolt to constitute a plurality of compression working spaces is housed in a closed container together with lubricating oil, and the lubricating oil is dispensed with the disk. A racer is formed so as to be able to flow from a central portion of the racer into the suction compression working chamber through a gap between the end faces of the displacer and communicate with the compressor suction port through a communication hole provided in the end plate. Can be achieved.

The second object is to dispose a displacer and a cylinder between end plates, and when the cylinder center and the displacer center are aligned, one space is formed by the cylinder inner wall surface and the displacer outer wall surface, In a displacement type fluid machine in which a plurality of spaces are formed when a positional relationship between the displacer and the cylinder is set at a swiveling position, a rotation shaft provided with an oil supply flow path for lubrication or the like is provided at a central portion of the displacer. Then, an electric element is provided on the rotating shaft, housed in a sealed container together with lubricating oil, a concave portion is provided on an end face of the displacer that moves in conjunction with the rotation of the rotating shaft, and a compressor inlet and the plurality of spaces are provided. A communication state may be established through a communication hole provided in the end plate and a suction flow path provided in the cylinder, or a flat surface may be provided substantially perpendicular to the axial direction of the rotating shaft. The suction channel of the plurality of spaces communicating with the by can be achieved by providing the cylinder.

[0012] Furthermore, a cylinder having an inner wall formed between the end plates and having a continuous curved surface in a plane shape, and an outer wall provided so as to face the inner wall of the cylinder, and the inner wall is provided with the inner wall when turning. In a displacement type fluid machine including the outer wall and a displacer forming a plurality of spaces by the end plate, a rotating shaft provided with an oil supply flow path for lubrication or the like is disposed at a central portion of the displacer, and At least a groove through which lubricating oil passes is provided between an end surface and an end plate of the displacer that moves in conjunction with rotation, and a suction hole provided in the cylinder and a communication hole provided with a compressor suction port and the plurality of spaces in the end plate. This can be achieved by forming a communication state via a flow path.

Further, a cylinder having an inner wall formed between the end plates and having a continuous curved surface in a plane shape, and an outer wall provided so as to face the inner wall of the cylinder, and the inner wall is provided with In a displacement type fluid machine including the outer wall and a displacer forming a plurality of spaces by the end plate, a rotation moment generated during operation of the machine is received by the displacer and the cylinder wall surface, and a compressor suction is performed. The mouth and the plurality of spaces may be configured to communicate with each other through a communication hole provided in an end plate and a suction channel provided in the cylinder, or the communication hole provided in the end plate may be seen through the direction of an axis of a rotating shaft. When viewed, the communication hole provided in the end plate is arranged on the cylinder and at a position intermittently arranged on the displacer with the rotation of the rotating shaft. It is achieved by the.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The features of the present invention described above will be further clarified by the following embodiments. Hereinafter, an embodiment of the present invention will be described with reference to the drawings. First, the structure of a positive displacement fluid machine according to an embodiment of the present invention will be described with reference to FIGS. FIG. 1A is a longitudinal sectional view (AA sectional view of FIG. 1B) showing a main part of a hermetic compressor when a positive displacement type fluid machine according to one embodiment of the present invention is used as a compressor. )
FIG. 2A is a plan view showing a state in which a compression chamber is formed as viewed in the direction of the arrow BB in FIG. 2A, FIG. 2 is a diagram showing the operation principle of the positive displacement compression element, and FIG. It is a longitudinal section of a hermetic compressor when used as a compressor.

In FIG. 1, a closed casing 3 accommodates a positive displacement element 1 and an electric element for driving the same (element 2 shown in FIG. 3). The details of the positive displacement compression element 1 will be described. FIG. 1B shows a triple wrap in which three sets of similar contour shapes are combined. The inner peripheral shape of the cylinder 4 is formed such that the hollow portion has a similar shape every 120 degrees (center o '). At the end of each hollow part, a plurality (in this case, 3
(There are three strip wraps). The displacer 5 is disposed inside the cylinder 4 and has a center shifted by ε so as to mesh with the inner peripheral wall 4a (a portion having a larger curvature than the vane 4b) of the cylinder 4 and the vane 4b. When the center o ′ of the cylinder 4 and the center o of the displacer 5 are matched,
It is configured such that a gap having a constant width is formed between the two contour shapes.

Next, the operation principle of the displacement type compression element 1 is shown in FIG.
And FIG. The symbol o is the center of the displacer 5, and the symbol o 'is the center of the cylinder 4 (or the rotating shaft 6). Symbols a, b, c, d, e, and f denote contact points at which the inner peripheral wall 4a and the vane 4b of the cylinder 4 mesh with the displacer 5. Here, looking at the inner peripheral contour shape of the cylinder 4, three combinations of the same curves are connected smoothly in succession at three locations. Focusing on one of these, the curve forming the inner peripheral wall 4a and the vane 4b can be regarded as one thick vortex curve (the tip of the vane 4b is considered to be the start of the vortex), and the inner wall curve ( g-a) means that the winding angle indicating the sum of the respective arc angles constituting the curve is approximately 360 degrees (the design concept is 360 degrees, but the value is not exactly that value due to manufacturing errors. The same applies hereinafter.) The winding angle is a vortex curve of the outer wall curve (g).
-B) is also a vortex curve with a winding angle of approximately 360 degrees. As described above, the one inner peripheral contour shape is formed from the inner wall curve and the outer wall curve. Arranged on these two curved circles at substantially equal pitches (120 degrees because of three wraps), the outer wall curve and the inner wall curve of the adjacent spiral body are connected smoothly with each other by a smooth connecting curve (bb ′) such as an arc. ), The entire inner peripheral contour shape of the cylinder 4 is formed. The outer peripheral shape of the displacer 5 is also configured in the same principle as that of the cylinder 4.

The spiral body composed of the three curves is arranged at a substantially equal pitch (120 degrees) on the circumference. This is for the purpose of uniformly distributing the load accompanying the compressing operation described later and for the purpose of manufacturing. In consideration of easiness, especially when these are not a problem, the pitch may be unequal.

Now, the compression operation by the cylinder 4 and the displacer 5 configured as described above will be described with reference to FIG. Reference numeral 7a denotes a suction port, that is, a communication hole provided in the end plate 7b, which is formed in a substantially circular shape. Reference numeral 8a denotes discharge ports, which are provided on end plates corresponding to three places, respectively.
(B) As shown in the figure, the contour of the communication hole 7a protrudes outside the outer wall surface of the displacer 5 when the compression working chamber 15 forms the maximum volume (corresponding to the area shown by hatching in the figure). Not formed. However, in consideration of the delay or advance of the compression operation, it may be formed so as to protrude from the outer wall surface of the displacer 5. Further, in the vicinity of the root of the vane 4b provided in the cylinder 4, the contour of the suction port, that is, the communication hole 7a provided in the end plate 7b can be configured to cover a part of the cylinder. Further, the size of the communication hole 7a can be reduced in consideration of the sealing performance between the displacer 5 and the end plates 7b and 8b and the pressure balance acting on both end surfaces of the displacer 5.

By rotating the rotating shaft 6, the displacer 5 revolves around the turning radius ε (= oo ′) without rotating around the center o ′ of the cylinder 4 on the fixed side. A plurality of compression working chambers are formed around o. The plurality of compression working chambers include an inner peripheral contour (inner wall) of the cylinder and an outer peripheral contour (side wall) of the displacer 5.
Means a space in which the suction is completed and a compression (discharge) process is performed among a plurality of closed spaces surrounded by That is, the space is a period from the end of suction to the end of discharge. If the above-mentioned winding angle is limited to 360 degrees, this space is lost at the end of compression, but at that moment, the suction ends, so this space is counted as one. However, when used as a pump, it refers to a space that communicates with the outside via a discharge port. In the embodiment, three compression working chambers are always formed.

A description will be given focusing on one hatched compression working chamber 15 surrounded by the contact points a and b. The compression working chamber 15 is divided into two at the end of the suction, but is a space where the two compression working chambers are connected and become one as soon as the compression stroke is started. FIG. 2A shows a state in which the suction of the working gas from the suction port 7a into the compression working chamber is completed. FIG. 2B shows a state in which the rotation shaft 6 is rotated 90 degrees from this state.
FIG. 2 (3) shows a state rotated by degrees, and FIG. 2 (4) shows a state rotated further by 270 degrees from the beginning. FIG.
When it is rotated 90 degrees from (4), it returns to the initial state of FIG. Thus, as the rotation proceeds, the volume of the compression working chamber 15 decreases and the discharge port 8a is closed by the discharge valve 9 (shown in FIG. 1), so that the working fluid is compressed. When the pressure in the compression working chamber 15 becomes higher than the external discharge pressure, the discharge valve 9 automatically opens due to the pressure difference, and the compressed working gas is discharged through the discharge port 8a. The rotation angle of the rotating shaft from the end of suction (compression start) to the end of discharge is 360 degrees, and the next suction stroke is prepared while each compression and discharge stroke is being performed. Starts compression. For example, contact a
Focusing on the space formed by and d, FIG.
At this stage, suction has already been started from the suction port (communication hole) 7a, and its volume increases as the rotation progresses.
In the state of (4), this space is divided. The fluid corresponding to the divided amount is supplemented from a situation indicating a state where the rotation angle is advanced, for example, a space when a space similar to the space formed by the contact points b and e is formed.

The manner of this supplement will be described in detail. FIG.
In the space formed by the contacts a and d adjacent to the compression working chamber formed by the contacts a and b in the state (1), suction has started. This space once expands like the space formed by the contacts a and d as shown in FIG. 2 (3), and is then divided at the contact d at the tip of the displacer when it becomes FIG. 2 (4). Therefore, for example, the contact point a in FIG.
All fluids in the space formed by (d) and (d) are
Are not compressed in the space formed by the contacts a and b. The same amount of fluid as the volume of the fluid that has been divided and not taken into the space formed by the contacts a and d is shown in FIG.
The space formed by the contacts b and e in the suction process in (4) is divided by the contact b as shown in FIG. 2A, and is formed by the contacts e and b near the discharge port. Filled by the fluid flowing into the space.

This is because the wraps are arranged at a uniform pitch as described above. That is, since the shapes of the displacer and the cylinder are formed by repeating the same contour shape, substantially the same amount of fluid can be compressed even if any compression working chamber obtains fluid from different spaces. Although it is possible to perform processing so that the volumes formed in the respective spaces are equal even if the pitch is not uniform, the productivity is poor. In any of the prior arts described above, the space in the suction process is closed and the internal fluid is compressed and discharged as it is, whereas the space in the suction process adjacent to the compression working chamber is divided. Performing the compression operation is one of the features of the present embodiment.

As described above, the compression working chambers for performing a continuous compression operation are distributed around the crank portion 6a of the rotating shaft 6 located at the center of the displacer 5 at substantially equal pitches. The compression working chambers are compressed out of phase. That is, when focusing on one space, the rotation angle of the rotating shaft is 360 degrees from the suction to the discharge, but in the present embodiment, three compression working chambers are formed,
Since the discharge is performed at a phase shifted by 20 degrees, when the compressor is operated as a compressor that compresses a gas as a fluid, the compressed gas is discharged three times during a rotation angle of the rotating shaft of 360 degrees.

If the space at the moment when the compression operation is completed (the space surrounded by the contact points a and b) is regarded as one space, if the winding angle is 360 degrees as in this embodiment, any compression Even in the machine operating state, the space in the suction stroke and the space in the compression stroke are designed to be alternated, so that the next compression stroke is started immediately after the compression stroke is completed. Fluid can be compressed smoothly and continuously.

Next, a compressor incorporating the volumetric compression element 1 having such a shape will be described with reference to FIGS. In FIG. 3, in addition to the cylinder 4 and the displacer 5 described above in detail, the positive displacement element 1 includes a rotating shaft 6 for driving the displacer 5 by fitting a crank part 6a to a bearing at the center of the displacer 5, A main bearing member 7 and a sub-bearing member 8, which also serve as bearings for supporting the rotating shaft 6 and an end plate for closing both end openings of the cylinder 4, and a suction port 7a (formed on an end plate 7b of the main bearing member 7). Communication hole 7a),
Discharge port 8 formed on end plate 8b of sub bearing member 8
a, a discharge valve 9 for opening and closing the discharge port 8a with a differential pressure. However, the discharge valve 9 may be of a reed valve type. On the other hand, the surface of the rotating shaft 6 or a bearing member rotatably supporting the rotating shaft 6 is subjected to a surface treatment in order to reduce friction loss due to sliding. Further, between the rotating shaft 6 and each of the bearing members 7 and 8, a bearing component made of a different material can be interposed. Further, the fitting portion between the rotating shaft 6 and the displacer 5 is configured in the same manner as described above. 5b is a through hole formed in the displacer 5. Reference numeral 10 denotes a suction cover attached to the main bearing member 7, and reference numeral 11 denotes a discharge cover for forming a discharge chamber 8c integrally with the sub-bearing member 8.

The displacement type compression element 1 is roughly classified into an end plate 7b provided with a suction port 7a (communication hole 7a), an end plate 8b provided with a discharge port 8a, a cylinder 4, a displacer 5, and a rotating shaft 6 , But all of these parts are manufactured as individual parts.

The end plate 7b and the end plate 8 are manufactured separately.
The surface where the end face of the cylinder 4 and the end face of the displacer 5 contact each other can be machined with high surface accuracy. Therefore, when operating as a compressor, there is an effect that the sealing property of the contact surface can be maintained high. Furthermore,
The machining accuracy of the curved wall surfaces of the cylinder 4 and the displacer 5 can be maintained high. Still another effect is that both end plates and cylinder 4
Since a fixing through hole is provided on the outer periphery of the unit for assembling, it is possible to assemble while assembling each part while performing positioning work with a high degree of freedom. Can be suitably maintained, and the flow resistance of the gas can be reduced.

The electric element 2 comprises a stator 2a and a rotor 2b, and the rotor 2b is fixed to the rotating shaft 6 by shrink fitting or the like. The electric element 2 is constituted by a brushless motor for improving electric motor efficiency, and is driven and controlled by a three-phase inverter. However, 2 may be another motor type, for example, a DC motor or an induction motor. Reference numeral 12 denotes lubricating oil stored at the bottom of the closed container 3, in which the lower end of the rotating shaft 6 is immersed. 13 is a suction pipe, 13a
Is a suction port, 14 is a discharge pipe, and 15 is the above-mentioned compression working chamber formed by the engagement between the inner peripheral wall 4a and the vane 4b of the cylinder 4 and the displacer 5. The discharge chamber 8b is separated from the pressure in the closed container 3 by a seal member 16 such as an O-ring.

The flow of the working gas (refrigerant gas) when the positive displacement fluid machine in this embodiment is used as an air conditioning compressor will be described with reference to FIG. As shown by the arrow in the figure, the working gas that has entered the sealed container 3 through the suction pipe 13 is supplied to the suction cover 10 attached to the main bearing member 7.
And enters the displacement type compression element 1 through the suction communication hole 7a. The rotation of the rotating shaft 6 causes the displacer 5 to perform a revolving motion to reduce the volume of the compression working chamber. You. The compressed working gas pushes up the discharge valve 9 through the discharge port 8a formed in the end plate 8b of the sub bearing member 8, enters the discharge chamber 8c, and flows out through the discharge pipe 14 to the outside. The reason why a gap is formed between the suction pipe 13 and the suction cover 10 is as follows.
This is for keeping the pressure in the closed vessel 3 low and for cooling the motor element 2 by circulating the working gas also in the motor element 2. Therefore, the pressure in the closed container 3 is kept substantially equal to the suction pressure.

The lubricating oil 12 stored inside is sent to each sliding portion from the bottom through a lubrication hole provided inside the rotating shaft 6 by a differential pressure or centrifugal pump lubrication to be lubricated. Part of this is also provided inside the compression working chamber 15 in the displacer 5 and the end plate 7.
b or 8b.

Here, an example of a method of forming the contours of the displacer 5 and the cylinder 4 which are the main components constituting the positive displacement compression element 1 of the present invention will be described with reference to FIGS. I will give you an example). FIG. 4 (a)
(B) is an example of the shape of the displacer whose planar shape is formed by a combination of arcs as an example, (a) is a plan view, and (b) is a side view. FIGS. 5A and 5B show FIG.
(A) is a plan view and (b) is a side view of an example of a cylinder shape which meshes with a pair of displacers shown in FIG. FIG. 6 is a diagram in which a center o of the displacer shown in FIG. 4 and a center o ′ of the cylinder shown in FIG.

In FIG. 4 (a), in the planar shape of the displacer, three identical contours are continuously connected around the center o (the center of the equilateral triangle IJK). The contour shape is formed by a total of seven arcs from the radius R1 to the radius R7, and the points p, q, r, s, t, u, v, w
Are connection points of arcs of different radii. The curve pq is
An arc of radius R1 centered on one side IK of the equilateral triangle, where point p is at a distance R7 from vertex I. The curve qr is an arc of a radius R2 having a center on an extension of a straight line connecting the connection point q and the center of the radius R1, and the curve rs is a connection point r and a radius R2.
Similarly, the curve st is a circular arc having a radius R3 having a center on a straight line connecting the connection point s and the center of the radius R3. The curve tu is an arc of a radius R5 having a center on an extension of a straight line connecting the connection point t and the center of the radius R4, and the curve uv is a connection point u and a radius R5
An arc having a radius R6 centered on a centroid o on an extension of a straight line connecting the centers of the circles is a radius R7 centered on a vertex J on a straight line connecting the connection point v and the center (centroid o) of the radius R6. Is an arc. Note that radii R1, R2, R3, R4, R5, R
The angle of each arc of No. 6 is determined by the condition that the connection is made smoothly at the connection point (the inclination of the tangent at the connection point is the same). When the contour from point p to point w is rotated 120 degrees counterclockwise around center o, point p overlaps point w, and further rotation by 120 degrees completes the contour around the entire circumference. This gives the displacer a planar shape,
The displacer is formed by giving the thickness h.

When the plane shape of the displacer is determined, when the displacer makes a revolving motion with a revolving radius ε, the contour of the cylinder meshed with the displacer becomes outside the curve constituting the contour of the displacer as shown in FIG. An offset curve having a normal distance of ε is obtained.

The outline shape of the cylinder will be described with reference to FIG. The triangle IJK is an equilateral triangle having the same size as that of FIG. The contour shape is formed by a total of seven arcs like the displacer, and the points p ′, q ′, r ′, s ′,
t ', u', v ', w' are connection points of arcs of different radii. A curve p′q ′ is an arc having a radius (R1−ε) centered on one side IK of an equilateral triangle, where the point p ′ is at a distance of (R7 + ε) from the vertex I. The curve q'r 'is an arc of a radius (R2-?) Having a center on an extension of a straight line connecting the connection point q' and the center of the radius (R1-?), And a curve r's'.
Is an arc having a radius (R3-ε) having a center on a straight line connecting the connection point r ′ and the center of the radius (R2-ε), and a curve s′t ′ is similarly a center of s ′ and the center of the radius (R3-ε). Is an arc of a radius (R4 + ε) having a center on a straight line connecting. The curve t′u ′ is an arc of radius (R5 + ε) having a center on an extension of a straight line connecting the connection point t ′ and the center of radius (R4 + ε), and the curve u ′
v ′ is an arc of a radius (R6 + ε) centered on a centroid o ′ on an extension of a straight line connecting the connection point u ′ and the center of the radius (R5 + ε), and a curve v′w ′ is a arc of a connection point v ′ and a radius (R6 + ε). ) Is an arc of a radius (R7 + ε) centered on a vertex J on a straight line connecting the center (center o ′).

Note that the radii (R1-ε), (R2-ε),
(R3-ε), (R4 + ε), (R5 + ε), (R6 +
Like the displacer, the angle of each arc in ε) is determined by the condition that the connection is made smoothly at each connection point (the inclination of the tangent at the connection point is the same). The contour shape from the point p 'to the point w' is represented by 12
When rotated 0 degrees, the point p 'coincides with the point w', and
When rotated by 0 degrees, the contour of the entire circumference is completed. Thereby, the planar shape of the cylinder is obtained. Cylinder thickness H
Is slightly thicker than the thickness h of the displacer.

FIG. 6 is a diagram showing a part of the center o of the displacer overlapped with the center o 'of the cylinder. The gap formed between the displacer and the cylinder is set to ε equal to the turning radius. It is desirable that this gap be ε over the entire circumference. However, for some reason, this gap is set within a range in which the compression working chamber formed by the outer peripheral contour of the displacer and the inner peripheral contour of the cylinder operates normally. There is no problem even if there is a place where is broken.

Although the method of forming the contours of the outer wall of the displacer and the inner wall of the cylinder by combining a plurality of circular arcs has been described here, the present invention is not limited to this, and the present invention is not limited to this. A similar contour shape can be formed by a combination of curves.

The operation and effect of the embodiment described with reference to FIGS. 1 to 6 will be described below. FIG. 7 shows another type of compressor in which the volume change characteristics of the compression working chamber (indicated by the ratio of the suction volume Vs to the compression working chamber volume V) in the present invention are plotted with the rotation angle θ of the rotary shaft from the end of suction as the horizontal axis. Shown in comparison with. Accordingly, the volume change characteristic of the positive displacement compression element 1 according to the present embodiment is as follows.
A kind of operating condition of an air conditioner having a discharge start volume ratio of 0.37 (for example, when the working gas is Freon HCFC22, the suction pressure P
s = 0.64 MPa, discharge pressure Pd = 2.07 MPa)
In comparison, the compression process is almost the same as the reciprocating type,
Since the compression process is completed in a short time, leakage of the working gas is reduced, and the capacity and efficiency of the compressor can be improved.
On the other hand, the discharge process is a rotary type (rolling piston type)
The pressure loss is reduced because the discharge flow velocity is slowed down by about 50%, and the fluid loss (excessive compression loss) in the discharge process can be greatly reduced to improve the performance.

FIG. 8 shows a change in the amount of work during one rotation of the rotating shaft, that is, a change in the gas compression torque T in this embodiment in comparison with other types of compressors (where Tm is the average torque). ). Thus, the torque fluctuation of the displacement type compression element 1 of the present invention is very small, about 1/10 of that of the rotary type, and is equivalent to that of the scroll type. Since there is no mechanism for performing the rotation, the vibration and noise of the compressor in which the inertia of the rotary shaft system is balanced can be reduced.

Further, as shown in FIG. 4, since the contour is not a long spiral shape as in the scroll type, the processing time and cost can be reduced, and an end plate for maintaining the spiral shape as in the scroll type. Since there is no (end plate), it can be manufactured by processing similar to a rotary type as compared with a scroll type which could not be processed by penetrating a jig. Further, since the thrust load due to the gas pressure does not act on the displacer, it is easy to manage the axial clearance which has an important effect on the performance of the compressor as seen in a scroll compressor, so that the performance can be improved.
Furthermore, as a result of the calculation, the thickness can be reduced as compared with a scroll compressor having the same volume and the same outer diameter, which can contribute to the reduction in size and weight of the compressor.

Next, the relationship between the above-mentioned winding angle and the rotation angle θc of the rotating shaft from the end of suction to the end of discharge will be described.
In the above-described embodiment, the winding angle is described as 360 degrees, but the rotation angle θc of the rotating shaft can be changed by changing the winding angle. For example, in FIG. 2, since the winding angle is 360 degrees, the rotation angle θc of the rotating shaft from the end of suction to the end of discharge returns to the original state when the rotation angle θc is 360 degrees. When the rotation angle θc of the rotating shaft from the end of suction to the end of discharge is reduced by making the winding angle smaller than 360 degrees, a state occurs in which the discharge port communicates with the suction port (communication hole), and the discharge port There is a problem that the fluid once sucked flows backward due to the expansion action of the fluid. 36 turns
If the angle is larger than 0 degree, the rotation angle of the rotating shaft becomes larger than 360 degrees, and two compression working chambers having different sizes are formed from the end of suction to the time of communication with the space having the discharge port. When this is used as a compressor, irreversible mixing loss occurs at the time of merging of the two because the pressure rises of these two compression working chambers are different from each other, and the compression power increases.
Further, even if it is used as a liquid pump, it is difficult to apply it as a pump because a compression working chamber that does not communicate with the discharge port is formed. For this reason, it can be said that the winding angle is desirably 360 degrees as much as possible within the range of allowable accuracy.

The rotation angle θc of the rotating shaft during the compression stroke in the fluid machine described in the above-mentioned Japanese Patent Application Laid-Open No. 55-23353 (Document 1) is θc = 180 degrees, and
The rotation angle θc of the rotating shaft in the compression stroke of the fluid machine described in Japanese Patent Application Laid-Open No. 869 (Reference 3) and Japanese Patent Application Laid-Open No. 6-280758 (Reference 4) is θc = 210 degrees. In the period from the end of the discharge of the working fluid to the start of the next compression stroke (end of suction), the rotation angle θ of the rotating shaft is described in Reference 1.
c is 180 degrees, and in References 3 and 4, it is 150 degrees.

When the rotation angle θc of the rotary shaft in the compression stroke is 210 degrees, each compression working chamber (reference I,
FIG. 9 (a) shows a compression stroke diagram of the compression strokes indicated by II, III and IV). However, the number of rows N = 4. The rotation angle θc of the rotating shaft is 3
Four compression working chambers are formed within 60 degrees, and the number n of compression working chambers simultaneously formed at a certain angle is n = 2.
Or it is 3. The maximum value of the number of compression working chambers formed at the same time is 3, which is smaller than the number of rows.

Similarly, FIG. 10A shows the case where the number of threads N = 3 and the rotation angle θc of the rotating shaft in the compression stroke is 210 degrees.
Also in this case, the number n of compression working chambers formed simultaneously is n = 1.
Alternatively, it is 2, and the maximum value of the number of compression working chambers formed at the same time is 2, which is smaller than the number of rows. In such a state, the compression working chamber is formed so as to be deviated around the rotation axis, so that a mechanical imbalance occurs, the rotation moment acting on the displacer becomes excessive, and the contact load between the displacer and the cylinder increases. There is a problem that performance is reduced due to an increase in mechanical friction loss and reliability is reduced due to vane wear.
In order to solve this problem, in the present embodiment, the rotation angle θc of the rotating shaft from the end of suction to the end of discharge (sometimes referred to as a compression stroke) is expressed as (((N−1) / N) · 360) <θc The outer peripheral contour of the displacer and the inner peripheral contour of the cylinder are formed so as to satisfy ≦ 360 (degrees) (Equation 1). In other words, the above-mentioned winding angle is in the range of Expression 1.

Referring to FIG. 9B, the rotation angle θc of the rotating shaft in the compression stroke is larger than 270 degrees, and the number n of compression working chambers formed at the same time is n = 3 or 4. The maximum value of the number of working chambers is four. This value corresponds to the number N of rows (= 4). In FIG. 10B, the rotation angle θc of the rotation shaft in the compression stroke is larger than 240 degrees, and the number n of compression working chambers formed simultaneously is n = 2.
Alternatively, it becomes 3, and the maximum value of the number of compression working chambers is 3.
This value is equal to the number N of rows (= 3).

As described above, the rotation angle θc of the rotation shaft in the compression stroke
Is made larger than the value on the left side of Expression 1, the maximum value of the number of compression working chambers becomes equal to or more than the number N, and the compression working chambers are dispersedly arranged around the rotation axis. As a result, the mechanical balance is improved, the rotation moment acting on the displacer is reduced, the contact load between the displacer and the cylinder is reduced, and the reliability of the contact portion can be improved as well as the performance is improved by reducing the mechanical friction loss.

On the other hand, the upper limit of the rotation angle θc of the rotating shaft in the compression stroke is 360 degrees according to the equation (1). The upper limit of the rotation angle θc of the rotation shaft in this compression stroke is 360 degrees. As described above, the time lag from the end of the discharge of the working fluid to the start of the next compression stroke (end of suction) can be set to zero, and the gas in the gap volume occurring when θc <360 degrees can be recovered. A reduction in suction efficiency due to expansion can be prevented, and an irreversible mixing loss that occurs when the two compression working chambers merge due to different pressure rises in the case of θc> 360 degrees can be prevented. . The latter will be described with reference to FIG.

FIG. 11 shows a displacement type fluid machine in which the compression stroke is 375 degrees at the rotation angle θc of the rotating shaft. FIG. 11 (a)
5 shows a state in which the suction of the two compression working chambers 15a and 15b in the drawing has been completed. At this time, the two compression working chambers 15a and 1
The pressure 5b is equal to the suction pressure Ps. The discharge port 8a is located between the compression working chambers 15a and 15b, and is not in communication with both compression working chambers. FIG. 11 shows a state in which the rotation has been advanced by 15 degrees at the rotation angle θc of the rotating shaft from this state.
(B). Discharge port 8a and both compression working chambers 15a and 15
This is the state immediately before b communicates. At this time, the compression working chamber 1
The volume of 5a is smaller than that at the end of the suction in FIG. 11A, the compression is progressing, and the pressure is higher than the suction pressure Ps. On the other hand, the volume of the compression working chamber 15b is larger than that at the end of suction, and the pressure is also lower than the suction pressure Ps due to the expansion action. When the next instantaneous compression working chambers 15a and 15b are united (communicated), irreversible mixing as shown by an arrow in FIG. 11C occurs, and performance decreases due to an increase in compression power. Therefore, the upper limit of the rotation angle θc of the rotation shaft in the compression stroke is 3
60 degrees is a desirable state.

FIGS. 12A and 12B show a compression element of a positive displacement fluid machine described in Document 3 or 4, wherein FIG. 12A is a plan view and FIG. 12B is a side view. The number of threads N is 3, and the rotation angle θc of the rotating shaft in the compression stroke is 210 degrees. In this figure, the number n of compression working chambers is n = as shown in FIG.
It becomes 1 or 2. This figure shows a state where the rotation angle θ of the rotation shaft is 0 degree, and the number n of compression working chambers is two. As is clear from this figure, the space on the right side of the space formed by the outer peripheral contour of the displacer and the inner peripheral contour of the cylinder does not serve as a compression working chamber, but instead has a suction port (communication hole) 7a and a discharge port. 8a communicates. For this reason, the gas once flowing into the compression working chamber of the cylinder 4 from the suction port (communication hole) 7a reversely flows due to the re-expansion of the gas in the clearance volume of the discharge port 8a, and there is a problem that the suction efficiency is reduced.

Now, let us consider a case where the rotation angle θc of the rotary shaft in the compression stroke of the positive displacement fluid machine shown in FIG. 12 is expanded by using the concept of the present embodiment. In order to increase the rotation angle θc of the rotation shaft in the compression stroke, the winding angle of the contour curve of the cylinder 4 must be increased as shown by a two-dot chain line. It is difficult to make the rotation angle θc of the rotation shaft of the compression stroke larger than 240 degrees so that the thickness becomes thin and the maximum value of the number n of the compression working chambers becomes equal to or more than the number N of rows (N = 3).

FIG. 13 shows an example of an embodiment of a compression element of a positive displacement fluid machine having the same stroke volume (suction volume), the same outer diameter, and the same turning radius as the positive displacement fluid machine shown in FIG. . The rotation angle θc of the rotation shaft in the compression stroke of the compression element shown in FIG.
Degree has been realized. This is because, in the compression element shown in FIG. 12, the gap between the seal points forming the compression working chamber is formed by a smooth curve, and therefore, for example, the rotation axis of the compression stroke is based on the concept of the present embodiment. Although a maximum of 240 degrees is the limit even if the rotation angle θc is to be increased, in the compression element according to the present embodiment shown in FIG. 13, the distance between the sealing points (ac) is not smooth (uniform curve). However, the shape near the contact point b is formed so as to protrude when viewed from the displacer, and a constriction exists in the middle of each strip of the displacer from the center to the tip. These are shown in FIG.
It can be said that the embodiment shown in FIG. With these shapes, the winding angle from the contact a to the contact b can be set to 24
The angle can be 360 degrees larger than 0 degrees, and the winding angle from the contact point b to the contact point c can be 360 degrees larger than 240 degrees. As a result, the rotation angle θc of the rotation shaft in the compression stroke can be set to 360 degrees which is larger than 240 degrees,
The maximum value of the number n of the compression working chambers can be set to the number N or more. For this reason, the compression working chambers are distributed and the rotation moment can be reduced.

Further, by increasing the number of compression working chambers that can function effectively, assuming that the cylinder height (thickness) of the compression element shown in FIG. 12 is H, the compression element shown in FIG. Is 0.7H, which is 30% lower, so that the size of the compression element can be reduced.

FIG. 14 is an explanatory diagram of the load and moment acting on the displacer 5 in the present embodiment.
The symbol θ is the rotation angle of the rotating shaft 6, and ε is the turning radius. With the compression of the working gas, a tangential force Ft perpendicular to the eccentric direction and a radial force Fr in the eccentric direction act on the displacer 5 due to the internal pressure of each compression working chamber 15 as shown in the figure. The resultant force of Ft and Fr is F. Due to the displacement of the resultant force F from the center o of the displacer 5 (length of the arm 1), a rotation moment M (= F · l) for rotating the displacer works. The rotation moment M is supported by contact points e and b of the displacer 5 and the cylinder 4.
Are the reaction force R1 and the reaction force R2. In the present invention,
Moment is received at two or three contact points near the suction port (communication hole) 7a, and no reaction force acts on the other contact points.

The displacement type compression element 1 of the present invention comprises a crank 6 a of a rotating shaft 6 fitted to the center of a displacer 5.
, The compression working chambers in which the rotation angle of the rotation shaft from the end of suction to the end of discharge is approximately 360 degrees at a substantially equal pitch are distributed, so that the point of action of the resultant force F is set to the center o of the displacer 5. , And the rotation moment M can be reduced by reducing the length l of the arm of the moment. Therefore, the reaction force R1 and the reaction force R2 are reduced. Also, as can be seen from the positions of the contact points g and b, the rotation mode
The sliding portion between the displacer 5 and the cylinder 4 receiving the pressure M is located near the suction port (communication hole) 7a of the working gas having a low temperature and a high oil viscosity, so that an oil film of the sliding portion is secured, and the friction is increased. A highly reliable positive displacement fluid machine that has solved the problem of wear can be provided.

FIG. 15 shows a comparison between the compression element shown in FIG. 12 and the compression element shown in FIG. 13 in terms of the rotation moment M acting on the displacer due to the internal pressure of the working fluid during one rotation of the shaft. The calculation condition is that the working fluid is HFC134a
Condition (suction pressure Ps = 0.095MP)
a, discharge pressure Pd = 1.043 MPa). Thus, in the compression element according to the present embodiment in which the maximum value of the number n of the compression working chambers is equal to or more than the number of rows, the compression working chambers from the end of the suction to the end of the discharge are arranged at a substantially equal pitch around the rotation axis. Therefore, the mechanical balance is improved, and the load vector due to compression can be configured to be substantially directed to the center. Therefore, the rotation moment M acting on the displacer can be reduced. As a result, the contact load between the displacer and the cylinder is reduced, so that the mechanical efficiency can be improved and the reliability as a compressor can be improved.

Here, the suction port (communication hole) 7a and the discharge port 8
The relationship between the period in which a is communicated and the rotation angle of the compression stroke rotation shaft will be described. The time lag Δθ represented by the rotation angle of the rotating shaft between the time when the suction hole and the discharge port communicate with each other, that is, from the end of the discharge of the working fluid to the start of the next compression stroke (end of suction) is represented by the rotation axis of the compression stroke. As the rotation angle θc of
Δθ = 360 degrees−θc. In the case of Δθ ≦ 0 degrees, there is no period in which the suction hole (communication hole) 7a communicates with the discharge port, so that the suction efficiency does not decrease due to the re-expansion of the gas in the gap volume of the discharge port. When Δθ> 0 degrees, since there is a period in which the suction hole (communication hole) 7a and the discharge port communicate with each other, the suction efficiency is reduced due to the re-expansion of the gas in the gap volume of the discharge port, and the compressor has (Refrigeration) capacity will be reduced. Further, a decrease in the suction efficiency (volume efficiency) leads to a decrease in the adiabatic efficiency, which is the energy efficiency of the compressor, or the coefficient of performance.

The rotation angle θc of the rotation shaft in the compression stroke is determined by the winding angle of the contour curve of the displacer or cylinder and the positions of the suction hole and the discharge port. When the winding angle of the contour curve of the displacer or the cylinder is set to 360 degrees, the rotation angle θc of the rotating shaft in the compression stroke can be set to 360 degrees, and θc <360 degrees by moving the seal point of the suction hole or the discharge port. Can also be. However, it is not possible to make θc> 360 degrees.

For example, the rotation angle θc = 375 degrees of the rotary shaft in the compression stroke of the compression element shown in FIG. 11 can be changed to θc = 360 degrees by changing the position and size of the discharge port. This can be realized by increasing the discharge port so that the compression working chamber 15a and the compression working chamber 15b communicate with each other immediately after the suction end state in FIG. By making such a change, θc = 37
The irreversible mixing loss caused by the difference in the pressure rise of the two compression working chambers that occurred at the time of 5 degrees can be reduced. Therefore, it can be said that the winding angle of the contour curve is a necessary condition for determining the rotation angle θc of the rotating shaft in the compression stroke, but is not a sufficient condition.

The embodiment described above, that is, FIG.
In the embodiment shown in (1), the closed type compressor in which the pressure in the closed casing 3 is maintained at a low pressure (suction pressure) has been described. However, the use of the low pressure type has the following advantages. (1) Since the electric element 2 is hardly heated by the compressed high-temperature working gas and cooled by the suction gas, the temperatures of the stator 2a and the rotor 2b are reduced, and the motor efficiency is improved and the performance is improved. Can be achieved. (2) In the case of a working fluid compatible with the lubricating oil 12 such as Freon, the pressure is low, so that the proportion of the working gas dissolved in the lubricating oil 12 is reduced. It is possible to improve the reliability of the sliding portion such as the above. (3) The pressure resistance of the sealed container 3 can be reduced, and the thickness and weight of the sealed container 3 can be reduced.

Next, a type in which the pressure in the sealed container 3 is maintained at a high pressure (discharge pressure) will be described. FIG.
FIG. 6 is an enlarged sectional view of a main part of a high-pressure hermetic compressor using a positive displacement fluid machine according to another embodiment of the present invention as a compressor. In FIG. 16, components denoted by the same reference numerals as those in FIGS. 1 to 3 are the same components and perform the same operations. In the drawing, reference numeral 13b denotes a suction chamber formed integrally with the main bearing member 7 by a suction cover 10, and a seal member 1 is provided.
6 and the like, the pressure (discharge pressure) in the closed container 3 is defined. Reference numeral 17 denotes a discharge passage communicating between the inside of the discharge chamber 8c and the inside of the closed container 3. The operation principle and the like of the positive displacement compression element 1 are the same as those of the low pressure (suction pressure) type described above.

The flow of the working gas flows through the suction pipe 13 and enters the suction port 13a as shown by the arrow in the drawing. The working gas flows through the suction port (communication hole) 7a formed in the main bearing member 7. Then, the displacement enters the displacement type compression element 1, where the rotation of the rotating shaft 6 causes the displacer 5 to perform a swiveling motion and the volume of the compression working chamber 15 is reduced, thereby being compressed. The compressed working gas pushes up the discharge valve 9 through the discharge port 8 a formed in the end plate of the sub-bearing member 8, enters the discharge chamber 8 c, passes through the discharge passage 17, and enters the closed container 3. It flows out from a discharge pipe (not shown) connected to the closed container 3.

The advantage of such a high pressure type is that lubricating oil 1
Since the pressure of 2 is high, the lubricating oil 12 supplied to each bearing sliding portion by the centrifugal pump action or the like due to the rotation of the rotating shaft 6 can be easily supplied into the cylinder 4 through a gap or the like at the end face of the displacer 5. Therefore, the sealing property of the compression working chamber 15 and the lubrication property of the sliding portion can be improved. that's all,
In the compressor using the positive displacement fluid machine of the present invention, it is possible to select either a low-pressure type or a high-pressure type according to the specifications and use of the equipment, production equipment, and the like, thereby greatly increasing the degree of freedom in design.

Next, the configuration of the suction passage according to the embodiment of the present invention will be described. FIG. 17 is an explanatory view showing one embodiment of the suction flow path, and FIG. 17 (1) shows one embodiment shown by the same cut as FIG. 1 (b). FIG. 17 (2) shows (1)
(A) is also a sectional view taken along the line BB in (2). Hereinafter, up to FIG. 21 shows another embodiment of the suction channel, but the type of the drawing is the same as that of FIG. Hereinafter, the configuration and operation will be described step by step.

In FIG. 17A, reference numeral 5c denotes a groove continuously provided on the end face of the displacer 5 from the central bearing portion 5a. 5
b is a concave portion provided so that the groove 5c is continuous. However, this space 5b may be a space communicating with the opposite end face in the same manner as the through hole shown in FIG. Displacer 5
The groove provided on the end surface of the second portion is continued to the concave portion 5d provided on the front end surface.

The grooves 5 c and the recesses are provided in the displacer 5.
, That is, on the end face of the end plate 8. Therefore,
When operating as a compressor, lubricating oil supplied via the rotating shaft is supplied from the inner surface 5a of the displacer 5 to each of the grooves 5c and the recesses 5b and 5d. As a result, an oil film easily exists in the gap between the displacer 5 and the end plates 7 and 8, keeping the sliding loss generated by the movement of the displacer 5 small and improving the sealing effect of the fluid in the compression working chamber 15. can do. Further, the thrust force in the rotation axis direction can be canceled by the pressure of the fluid acting on both end surfaces of the displacer 5.

The communication hole 7a provided in the end plate 7 communicates with a suction passage 4f provided in the cylinder 4, and grooves 4g, 7g, 8g are provided so as to be orthogonal to the passage. Therefore, the suction gas flows into the compression working chamber from the circumferential direction. As a result, the inertia force of the suction gas flows into the compression working chamber from the suction process to the compression stroke.

Further, since the position of the suction port shown in FIG. 1 is arranged so as not to overlap with the displacer 5, the lubricating oil can be held up to the tip of the displacer 5 and the sealing performance can be improved. Therefore, the volume efficiency of the compressor can be improved. Further, even if the rotation moment acts on the displacer 5 and the moment is received by the arc portion of the cylinder 4 and the displacer 5, the suction passage 4 f is provided on the outer peripheral side of the arc portion of the cylinder 4. Although the contact area of the displacer 5 on the wall portion is reduced, the position receiving the moment moves toward the other vanes, and the contact load is reduced, so that the preferable state of the turning motion is not impaired. Next, still another embodiment will be described with reference to FIG. The basic configuration of the figure is similar to that of FIG. 17 but different points are described below. In this embodiment, the suction flow path is bent in the cylinder 4 toward the displacer 5. In this embodiment,
Since the suction gas collides with the side surface of the displacer 5, it is possible to prevent the suction gas from directly entering the gap between the both end faces, so that the sealing effect at the end face can be kept high. Further, the tip of the displacer 5, that is, the portion receiving the moment load, is suitably cooled by the suction gas, so that the viscosity of the lubricating oil leaked from the gap between the end surfaces increases, so that the reliability at the contact portion increases, and The sealing effect of the working gas can be kept high.

Next, still another embodiment will be described with reference to FIG. The basic configuration of the figure is similar to that of FIG. 17 but different points are described below. In this embodiment, a part of the suction passage 4f is arranged so as to overlap the compression working chamber side. The flow path 4h is provided to be longer than the thickness of the displacer 5, and the end plate 8 is formed as a recess 8g. In FIG. 17, similarly, a concave portion is provided in the end plate. However, the concave portion 8g also has an effect of a dust collecting groove for preventing foreign substances and the like flowing together with the suction gas from entering the compression working chamber 15. Further, according to the present embodiment, since the suction flow path 4h is arranged so as to interfere with the compression working chamber 15, the suction pressure loss can be suppressed to a small value, and a sufficient amount of suction gas can be secured.

FIG. 20 shows still another embodiment. In the present embodiment, the suction flow path 4h is formed halfway through the displacer 5. In this case, the processing is simple, the pressure loss is small, and the lubricating oil can be held in the oil pockets 5d and the oil grooves 5c at both end surfaces of the displacer 5.
Further, the contact area between the displacer 5 and the wall surface of the cylinder 4 can be maintained to a considerable extent in the same manner as the flow path shown in FIG. 17, so that a rotation moment can be received, and therefore the position of the suction flow path 4h or 4f Can be provided more centrally, and a more sufficient amount of gas can be supplied also to the compression working chamber 15b.

FIG. 21 shows still another embodiment, and shows an example of arrangement in a case where the displacer 5 and the cylinder 4 are formed in four rows. The suction flow path 4h is shown in FIG.
However, any of the flow path configurations shown in FIGS. 17 to 19 can be employed. The effect at that time is almost the same.

Next, another embodiment according to the present invention will be described with reference to FIG. . In FIG. 22, the displacement type compression element 1
In addition to the cylinder 4 and the displacer 5 described above in detail, the crank part 6 is mounted on a bearing at the center of the displacer 5.
a rotating shaft 6 for driving the displacer 5 with a fitted therein, a main bearing member 7 provided with an end plate for closing both end openings of the cylinder 4 and bearings 71 and 72 for supporting the rotating shaft 6; Sub-bearing member 8 provided with a bearing 81 for supporting the shaft 6, and a suction port 7a formed in an end plate 7b of the main bearing member 7.
(Communication hole 7a), a discharge port 8a formed in the end plate 8b of the auxiliary bearing member 8, and a discharge valve 9 for opening and closing the discharge port 8a with a differential pressure. However, the discharge valve 9 may be of a reed valve type. Further, the fitting portion between the rotating shaft 6 and the displacer 5 is also provided with a bearing 5a in the same manner as described above.
5b is a through hole formed in the displacer 5. 10 is a suction cover attached to the main bearing member 7,
Reference numeral 11 denotes a discharge cover for forming a discharge chamber 8c integrally with the auxiliary bearing member 8. According to this, various materials for the bearing can be selected, so that the reliability of the drive mechanism such as the bearing can be maintained high even under various operating conditions.

FIG. 23 shows an air conditioning system to which the positive displacement compressor of the present invention is applied. This cycle is a heat pump cycle capable of cooling and heating, and includes the positive displacement compressor 30, the outdoor heat exchanger 31, and the fan 3 of the present invention described with reference to FIG.
1a, expansion valve 32, indoor heat exchanger 33 and its fan 33
a, a four-way valve 34. An alternate long and short dash line 35 indicates an outdoor unit and 36 indicates an indoor unit. The positive displacement compressor 30 operates according to the operation principle diagram shown in FIG. 2, and starts up the cylinder 4 and the displacer 5 by starting the compressor.
Working fluid (eg, CFC HCFC22 or R407)
C, R410A, etc.).

In the cooling operation, the compressed high-temperature and high-pressure working gas is supplied from the discharge pipe 14 to the
After flowing into the outdoor heat exchanger 31 through the direction valve 34, the heat is radiated and liquefied by the blowing action of the fan 31a, throttled by the expansion valve 32, and adiabatically expanded to a low temperature and low pressure.
After absorbing the indoor heat and gasifying it, the suction pipe 13
, And is sucked into the positive displacement compressor 30. On the other hand, in the case of the heating operation, as indicated by the solid arrow, the air flows in the opposite direction to the cooling operation, and the compressed high-temperature and high-pressure working gas is discharged from the discharge pipe 14.
Flows through the four-way valve 34 into the indoor heat exchanger 33, radiates heat into the room by the blowing action of the fan 33a, liquefies, is squeezed by the expansion valve 32, adiabatically expands to low temperature and low pressure, After the heat is absorbed from outside air and gasified by the exchanger 33,
It is sucked into the positive displacement compressor 30 via the suction pipe 13.

FIG. 24 shows a refrigeration system equipped with the positive displacement compressor of the present invention. This cycle is a cycle dedicated to freezing (cooling). In the figure, 37 is a condenser, 37
a is a condenser fan, 38 is an expansion valve, 39 is an evaporator, 39
a is an evaporator fan. By starting the positive displacement compressor 30, the working fluid is compressed between the cylinder 4 and the displacer 5, and the compressed high-temperature and high-pressure working gas flows from the discharge pipe 14 to the condenser 37 as shown by the solid arrow.
And radiated and liquefied by the blowing action of the fan 37a,
Squeezed by the expansion valve 38, adiabatically expanded to a low temperature and low pressure,
After being endothermic gasified by the evaporator 39, it is sucked into the positive displacement compressor 30 through the suction pipe 13. Since the displacement compressor of the present invention is mounted in both FIGS. 23 and 24,
A highly reliable refrigeration / air-conditioning system with excellent energy efficiency, low vibration and low noise can be obtained. Although the low-pressure type is described as an example of the positive displacement compressor 30 here, the high-pressure type also functions in the same manner and has the same effect.

Next, another embodiment of the present invention will be described. FIG. 25 is a longitudinal sectional view of a main part using a positive displacement fluid machine according to another embodiment of the present invention as a pump (FIG. 26).
26 is a view taken along the line BB of FIG. 25. Note that components denoted by the same reference numerals as those in FIGS. 1 to 3 are the same components and perform the same operations.

In the figure, reference numeral 40 denotes a fixed side member, which comprises a fixed spiral body 40a, an end plate 40b, and a main bearing 40c, and each part is integrally formed. Reference numeral 41 denotes a revolving-side member, a revolving spiral 41a, a reinforcing plate 41b for connecting the revolving spiral 41a at an outer peripheral portion near an axial center of the revolving spiral, and a revolving spiral 41.
It is composed of a bearing 41c disposed at the center of the line a. Reference numeral 42 denotes a ring portion that surrounds the outer periphery of the fixed-side spiral body 40a, forms a suction chamber 42a therein, and communicates with the outside through a suction port 42b. 43 is a check valve, and 44 is a shaft sealing device. Also 4
Reference numeral 5 denotes a compression working chamber formed by meshing of the fixed scroll 40a and the revolving scroll 41a. The symbol Om is the center of the turning side member 41 which is a displacer, and the symbol Of is the center of the fixed side member 4 (or the rotating shaft 6). Here, the fixed side member 40 has fixed spiral bodies 40a having a winding angle of about 360 degrees arranged at three places (at least two places) on the end plate portion 40b and at substantially equal pitches around the center Of. The shape of the revolving spiral 41a of the revolving-side member 41 is determined so as to satisfy the meshing relationship with the fixed spiral 40a.

The flow of the working fluid (incompressible liquid in this example) flows through the suction port 42b formed in the ring portion 42 as shown by the arrow in FIG. The rotating shaft 6 is driven by an electric element (not shown).
Are rotated, and the swiveling member 41 is swirled to be sucked into the compression working chamber 45. The volume of the compression working chamber 45 is reduced, so that the swiveling member 41 moves and is discharged on the end plate of the auxiliary bearing member 8. Through the port 8a into the discharge chamber 8b,
It is conveyed outside through the check valve 43 and the discharge pipe 14. In this embodiment, the basic operation principle is the same as that of the positive displacement compression element 1 described with reference to FIG. The difference between the two is that since the working fluid is a non-compressible liquid, the discharge stroke starts next at the same time as the end of suction. Further, the volume change characteristic of the compression working chamber 45 and the shaft 1 when the gas is compressed.
The change in the gas compression torque T during rotation is the same as in FIGS. 7 and 8. Therefore, it is possible to significantly reduce the fluid loss (excessive compression loss) in the discharge process, improve the performance, and reduce the vibration and noise. .

As described above, the fixed spiral body 40a having a winding angle of substantially 360 degrees is formed on the end plate portion 40b of the fixed side member 40.
Although the displacement type fluid machine having the parts has been described, the present invention is not limited to this, and the number of the fixed spiral bodies 40a is two or more and N (multiple) as in the above-described embodiment.
(The value of N is practically 8 to 10 or less as in the above-described embodiment).

In the embodiments described above, the compressor and the pump are described as examples of the positive displacement fluid machine. However, the present invention can be applied to an expander and a power machine. Further, in the present invention, one (cylinder side) is fixed and the other (displacer) performs a revolving motion without rotating at a substantially constant turning radius, but is relatively equivalent to the above motion. The present invention can also be applied to a double-rotation type positive displacement fluid machine that has a simple movement form.

[0080]

As described above in detail, according to the present invention, two or more compression working chambers are arranged around the rotation axis, and the end of the suction and the end of the discharge of each compression working chamber are provided. By setting the rotation angle of the rotating shaft to be approximately 360 degrees, the overcompression loss during the discharge process is greatly reduced, and the rotation moment acting on the displacer is reduced to reduce the friction loss between the displacer and the cylinder. By doing so, a positive displacement fluid machine with improved performance and high reliability can be obtained. In addition, by mounting such a positive displacement fluid machine on a refrigeration cycle, a highly reliable refrigeration / air-conditioning system with excellent energy efficiency can be obtained.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view and a plan view of a compression element of a hermetic compressor in which a positive displacement fluid machine according to the present invention is applied to a compressor.

FIG. 2 is an explanatory view of the operation principle of the positive displacement fluid machine according to the present invention.

FIG. 3 is a longitudinal sectional view of a positive displacement fluid machine according to the present invention.

FIG. 4 is a diagram showing a contour configuration method of a displacer of the positive displacement fluid machine according to the present invention.

FIG. 5 is a diagram showing a method of forming a contour of a cylinder of the positive displacement fluid machine according to the present invention.

FIG. 6 is a diagram in which the displacer and the cylinder shown in FIGS. 4 and 5 are superimposed.

FIG. 7 is a diagram showing a volume change characteristic of a compression working chamber in the present invention.

FIG. 8 is a graph showing a change in gas compression torque according to the present invention.

FIG. 9 is a view showing the relationship between the rotation angle of the rotation shaft and the compression working chamber in the four-row wrap.

FIG. 10 is a view showing the relationship between the rotation angle of the rotation shaft and the compression working chamber in the three-row wrap.

FIG. 11 is an operation explanatory diagram when the winding angle of the compression element is larger than 360 degrees.

FIG. 12 is a view for explaining an enlargement of a winding angle of a compression element.

FIG. 13 is a modified example of the positive displacement fluid machine shown in FIG. 1;

FIG. 14 is a diagram illustrating loads and moments acting on the displacer of the present invention.

FIG. 15 is a diagram showing a relationship between a rotation angle of a rotation shaft of a compression element and a rotation moment ratio.

FIG. 16 is a vertical sectional view of a main part of a hermetic compressor according to another embodiment of the present invention.

17A and 17B are a plan view and a cross-sectional view illustrating an arrangement of a suction flow channel according to an embodiment of the present invention.

FIG. 18 is a plan view and a cross-sectional view showing an arrangement of a suction flow channel according to another embodiment of the present invention.

FIG. 19 is a plan view and a cross-sectional view illustrating an arrangement of a suction flow channel according to another embodiment of the present invention.

FIG. 20 is a plan view and a cross-sectional view showing an arrangement of a suction flow channel according to another embodiment of the present invention.

FIG. 21 is a plan view and a cross-sectional view showing an arrangement of a suction flow channel according to another embodiment of the present invention.

FIG. 22 is a longitudinal sectional view of a main part of a hermetic compressor according to another embodiment of the present invention.

FIG. 23 is a diagram showing an air conditioning system to which the positive displacement compressor of the present invention is applied.

FIG. 24 is a diagram showing a refrigeration system to which the positive displacement compressor of the present invention is applied.

FIG. 25 is a vertical cross-sectional view of a main part using a positive displacement fluid machine according to another embodiment of the present invention as a pump.

FIG. 26 is a cross-sectional view taken along the line BB of FIG. 25.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Displacement type compression element 2 Electric element 3 Airtight container 4 Cylinder 4a Inner peripheral wall 4b Vane 5 Displacer 5a Bearing 5b Through hole 6 Rotating shaft 6a Crank part 7 Main bearing support member 7a Suction port (communication hole) 7b End plate 8 Sub bearing support Member 8a Discharge port 8b End plate 8c Discharge chamber 9 Discharge valve 10 Suction cover 11 Discharge cover 12 Lubricating oil 13 Suction pipe 13a Suction port 14 Discharge pipe 15 Compression operating chamber 16 Seal member 17 Discharge passage 30 Displacement compressor 31 Outdoor heat exchange Device 32 Expansion valve 33 Indoor heat exchanger 34 Four-way valve 37 Condenser 38 Expansion valve 39 Evaporator 40 Fixed side member 40a Fixed spiral body 40b End plate section 40c Main bearing section 41 Revolving side member 41a Revolving spiral body 41b Reinforcement plate 41c Bearing 42 Ring part 42a Suction chamber 42b Suction port 43 Check valve 4 Shaft seal device 45 compressed working chamber o displacer center o 'cylinder center

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Kunihiko Takao 502 Kandachi-cho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratory, Hitachi, Ltd. (72) Inventor Hiroaki Hata 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Hitachi, Ltd. (72) Inventor: Shigetaro Tagawa 800, Tomita, Ohira-machi, Ohira-cho, Shimotsuga-gun, Tochigi In-house: Hitachi, Ltd.Cooling and Heating Division (72) Inventor: Kenji Tojo 390, Muramatsu, Shimizu, Shizuoka Prefecture, Ltd., Air Conditioning System Division, Hitachi, Ltd.

Claims (9)

[Claims] 1. A displacer and a cylinder are disposed between end plates, and when the cylinder center and the displacer center are aligned, one space is formed by the cylinder inner wall surface and the displacer outer wall surface, and the displacer and the cylinder are formed. In a positive displacement fluid machine in which a plurality of spaces are formed when the positional relationship with the swirling position is established, a compressor suction port, a communication hole provided in the end plate with the plurality of spaces, and a suction passage provided in the cylinder A positive displacement fluid machine characterized in that the fluid machine is configured to be in communication with the fluid machine. 2. A displacer and a cylinder are arranged between end plates, and when the cylinder center and the displacer center are aligned, one space is formed by the cylinder inner wall surface and the displacer outer wall surface, and the displacer and the cylinder are formed. In a displacement type fluid machine in which a plurality of spaces are formed when the positional relationship with the turning position is set, an end plate having a suction flow path and an end plate having a discharge flow path,
A cylinder enclosing a flat displacer disposed between both end plates is provided, and a rotary shaft having a crank portion is disposed at a substantially central portion of the cylinder, and the both end plates and the cylinder are integrally formed by fastening means. A positive displacement fluid machine characterized in that: 3. A displacer and a cylinder are disposed between end plates, and when the cylinder center and the displacer center are aligned, one space is formed by the cylinder inner wall surface and the displacer outer wall surface, and the displacer and the cylinder are formed. In the displacement type fluid machine in which a plurality of spaces are formed when the positional relationship with the swirling position is established, a rotation shaft is disposed at the center of the displacer, and a compression mechanism unit including the plurality of spaces and the like. And a passage through which the lubricating oil flows from a central portion of the displacer into a suction compression working chamber through a gap between end faces of the displacer, and a compressor suction port and the plurality of compressors. A positive displacement fluid machine characterized in that a space is communicated through a communication hole provided in an end plate. 4. A displacer and a cylinder are arranged between end plates, and when the cylinder center and the displacer center are aligned, one space is formed by the cylinder inner wall surface and the displacer outer wall surface, and the displacer and the cylinder are formed. In the displacement type fluid machine in which a plurality of spaces are formed when the positional relationship with the rotating position is established, a rotating shaft provided with an oil supply flow path for lubrication or the like is disposed at the center of the displacer, and the rotating shaft is An electric element is provided in the sealed container together with the lubricating oil, and a concave portion is provided on an end face of the displacer which moves in conjunction with the rotation of the rotating shaft, and a compressor inlet and the plurality of spaces are provided on an end plate. A positive displacement fluid machine characterized in that it is configured to communicate with a communication hole via a suction passage provided in the cylinder. 5. A positive displacement fluid machine according to claim 1, wherein said cylinder has a suction flow passage communicating with said plurality of spaces in parallel with a plane substantially orthogonal to an axial direction of a rotating shaft. A positive displacement fluid machine characterized by being provided. 6. The displacement type fluid machine according to claim 1, wherein a position of the suction flow path is located outside of a portion having a curvature of a root of the vane on the cylinder side and receiving a rotation moment of the displacer. A positive displacement fluid machine characterized by the following. 7. A cylinder having an inner wall formed between the end plates and having a continuous curved plane, and an outer wall provided so as to face the inner wall of the cylinder. In a displacement type fluid machine including an outer wall and a displacer forming a plurality of spaces by the end plate, a rotating shaft provided with an oil supply flow path for lubrication or the like is disposed at a center of the displacer, and rotation of the rotating shaft is performed. A groove portion through which at least lubricating oil passes is provided between an end face and an end plate of the displacer which moves in conjunction with the suction port, a communication hole provided with a compressor suction port and the plurality of spaces in the end plate, and a suction flow provided in the cylinder. A positive displacement fluid machine characterized by being configured to be in communication with a road. 8. A cylinder having an inner wall formed between a pair of end plates and having a continuous curved planar shape, and an outer wall provided so as to face the inner wall of the cylinder. In a displacement type fluid machine including an outer wall and a displacer forming a plurality of spaces by the end plate, a rotational moment generated during operation of the machine is received by the displacer and the cylinder wall surface, and a compressor suction port is provided. And the plurality of spaces are communicated with each other through a communication hole provided in an end plate and a suction passage provided in the cylinder. 9. The displacement type fluid machine according to claim 1, wherein when the communication hole provided in the end plate is viewed from the axial direction of the rotation shaft, the communication hole provided in the end plate is the cylinder. A positive displacement fluid machine, wherein the fluid machine is arranged on the displacer intermittently with the rotation of a rotating shaft.