WO1994008140A1

WO1994008140A1 - Compressor

Info

Publication number: WO1994008140A1
Application number: PCT/JP1993/000448
Authority: WO
Inventors: Hideo Kaji
Original assignee: Hideo Kaji
Priority date: 1992-10-01
Filing date: 1993-04-07
Publication date: 1994-04-14

Abstract

A compressor wherein a stator (13) as an outside relatively rotating member is disposed in a cylindrical casing (4) in such a manner as not to rotate therein, and wherein a runner (14) as an inside relatively rotating member is provided on the inner side of said stator (13) in such a manner as to freely move in a circular fashion. The runner (14) has a shaft center (G) made eccentric by an eccentric amount (e) relative to the shaft center (F) of the stator (13) and is supported by a crank pin (3a) of a crank shaft (3) driven by a motor (M). The stator (13) has a circumferential wall (13c) and leading end projections (27) inwardly projecting from the sides of the wall. The leading end projections (27) are located on imaginary circles each having a radius (R2), and the contour of the circumferential wall (13c) is constituted by a concaved arc having a radius (R5) and another concaved arc smoothly continuing from the concaved arc and having a radius (R6). The runner has semi-circular vanes (25) extending radially outwardly from its shaft center. The runner defines a sealed compression chamber (24) on the innerside of the circumferential wall of the stator, and the volume of this compression chamber varies as the runner rotates, and fluid sucked into the compression chamber (24) via a suction port (13a) is discharged via a discharge port (14b). This compressor is quiet in operation and easy to work with. The stator (13) may be constructed as a rotation-driven outside runner. In this case, the inside runner is rotated and driven by the rotation of the outside runner.

Description

Akira glue

Composer

Technical field

The present invention relates to a compressor, and more particularly, to a compressor which is small in vibration and easy to process. Incidentally, the compressor of the present invention includes a pump.

North

冃

Skill

Conventionally, the compressor is a piste technique in a cylinder.

Reciprocating compressors and casings that compress the gas such as refrigerant gas in the cylinder by the reciprocating motion of the compressor. The rotating piston tanker, which is mounted eccentrically in the cylinder, keeps contact between the inner surface of the cylinder and the cutting edge at the tip of the slide vane. On the other hand, there is generally known a rotor-slipton type compressor which performs a compression action by rotating on a constant eccentric path. . However, in the case of the reciprocating compressor, the reciprocating compressor is reciprocating in the piston casing cylinder. Because of the motion or the eccentric rotation, it does not become a source of vibration and noise, but leads to loss of inertia energy and friction energy. There was a problem that the efficiency was getting worse. Therefore, the two scrolls are set out of phase with each other by 180 °, and one of the scrolls is fixed and the other is fixed. When a scroll is made to move in a circle, the space formed between the two scrolls moves from the outside toward the center while the volume of the space decreases. By utilizing this, a scroll-type compressor that compresses gas such as refrigerant gas has been developed.

This scroll type compressor operates smoothly because the drive torque fluctuation is relatively small and the fluctuation is gradual. It is not only very quiet but also able to operate at high speed, and because the approach between the scrolls is close to the surface, it is possible to obtain high volumetric efficiency. It has the characteristic of

In the above-mentioned scroll-type compressor, the compression force is formed between two scrolls from the structure and used for compression. The volume of the space to be removed is relatively small, the amount of gas discharged by one rotation of the scroll is small, and the scroll has high precision. There was a problem that the power was very troublesome.

SUMMARY OF THE INVENTION In view of the above, the present invention can provide a small and large discharge while maintaining the advantages of a scroll-type compressor. The purpose of which is to provide a compressor that can easily perform high-precision machining with little vibration o

— — Disclosure of the invention

In order to achieve the above object, a compressor according to the present invention comprises an outer relative rotation member having a first axis and an eccentric parallel to the first axis. An inner relative rotation member having a second axis and located inside the outer relative rotation member; and the outer relative rotation member and the inner relative rotation member, the first relative rotation member being the first relative rotation member. A means for supporting the second shaft center so as to be relatively rotatable while maintaining a eccentric distance, and a means for relatively rotating the two relative rotating members. The relative rotating member has at least one peripheral wall having a partial cylindrical shape, and a distal end protruding inward from the peripheral wall so as to approach the first axis. The inner relative rotation member has at least one member extending outward from the second axis. It has an arc plate-shaped arc vane, and by this arc vane, a closed space is formed inside the peripheral wall, and the volume of the closed space is increased by the relative rotation member. The discharge port is provided at a position where the volume becomes zero, and the suction port is provided at a part of the peripheral wall. And

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is an axial sectional view of a first embodiment of the compressor of the present invention.

FIG. 2 is an enlarged end view in the axial direction of the stay in the first embodiment. Figure 3 is Ru Ah in enlarged axial end view of the run-Na you only that in the first example ₀

FIG. 4 is an enlarged axial end view showing a state where the stay and the runner in the first embodiment are combined.

FIGS. 5A, 5B, 5C, and 5D are schematic cycle diagrams showing sequential operation states of the compressor of the first embodiment.

Figure 6 is a plan view of the casing.

FIG. 7 is a diagram viewed in the axial direction showing a state in which a stay and a runner according to the second embodiment of the present invention are combined.

FIG. 8 is a sectional view of a compressor according to a second embodiment of the present invention, taken along the entire axial direction.

Fig. 9 is an axial end view of the runner in the second embodiment.

FIG. 10 is an axial sectional view of the runner shown in FIG. Fig. 11 shows the axial end view of the stay in the second embodiment.

(J'me.

FIG. 12 is an axial cross-sectional view of the stator shown in FIG. 11, and FIG. 13 is an explanatory diagram showing a design method of the stator. FIG. 14 is an axial sectional view of a compressor according to a third embodiment of the present invention.

FIG. 15 is an enlarged axial end view of the outer runner of the compressor of FIG.

FIG. 16 is an enlarged free end view of the inner runner of the compressor of FIG. FIG. 17 is an enlarged end view in the axial direction in a state where the outer runner and the inner runner of FIGS. 15 and 16 are combined.

FIG. 18 is a plan view of the compressor of FIG.

FIG. 19A, FIG. 19B, FIG. 19C, and FIG. 19D are explanatory diagrams sequentially showing the changing operating states of the compressor of FIG.

FIG. 20 is a view similar to FIG. 7 showing a fourth embodiment which is a modification of the third embodiment.

FIGS. 21A, 21B, 21C, and 21D are schematic cycle diagrams sequentially showing the operation state of the fourth embodiment.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view of a compressor according to a first embodiment of the present invention in the whole axial direction. In FIG. 1, the compressor 1 includes: A cylindrical joint 2 for connecting the motor M is provided, and a crankshaft 3 arranged in the joint 2 has an end portion of the motor M that is connected to the cylindrical joint 2. An output shaft (not shown) is connected so that the rotational force of the motor is transmitted to the crankshaft 3 of the compressor 1. .

The joint 2 is connected to the end surface of the casing 4 via a bolt 5 at the flange portion 2a to close the opening. The front end plate 6 is connected to the front end plate 6 via a bonolet 7, and is connected between the front end plate 6 and the joint 2 and the front end plate. End Bracket 6 and Case 4 And rubber packs 8 and 9 are interposed between them.

A bearing 10 is held in the center of the front blade 6 described above, and the crankshaft 3 is fixed by the bearing 10. In addition to being supported by the force rotation itself, two pairs of large and small baluns are provided on both sides of the shaft 3 in the axial direction of the crankshaft 3.ゥゥ Units 11 and 12 are placed so that they cannot escape. In addition, a crank pin 3a is provided on the opposite side of the crank shaft 3 from the motor M, and the crank pin 3a. The shaft 3 and the eccentric amount e of the crank shaft 3 are arranged so as to protrude in an eccentric state only by the eccentric state, and as a result, the crank shaft rotates with the rotation of the motor. By the rotation of the shaft 3, the crank pin 3a revolves with the eccentricity e as a radius from a force that does not rotate.

As described above, it is the crankshaft 3 that has two large and small balance weights 11 and 12 on both sides of the bearing 10 in the crankshaft 3. This is to improve the balance when rotating the shaft 3 (revolution).

The inside of the casing 4 described above has a substantially cylindrical stay force 13 <the center of which is matched with the axis F of the crank shaft 3. The stator 14 is fixed and arranged in a state where the runner 14 is removed from the inside of the stator 13 by a hollow circular fixing plate 15. The runner 14 housed and stored so as not to be able to come out constitutes an inner relative rotating member. Night 13 can also be driven to rotate relative to the runner 14 as in the embodiment described later, so that it constitutes an outer relative rotating member.

The end of the runner 14 on the motor M side has a flange section.

1 4 a Force <A stage that is installed and fixed to the casing 4 so that the flange portion 14 a is sandwiched. The fixing plate 15 fixed to the evening 13 is arranged.

The corresponding positions of the surface of the flange portion 14a on the fixing plate 15 side and the surface of the flange portion 14a of the fixing plate 15 side are respectively corresponding to the fixing plate 15a. A plurality of recesses 14 b and 15 a (in the figure, a total of six) are provided along the circumferential direction, and each of the recesses 14 facing each other is provided. In b, 15a, a circular bearing 16 is housed.

The circular bearing 16 is used for positioning the stay 13 and the runner 14 and for displacing the relative displacement of the both 13 and 14. This is for the purpose of making each recess 14 b

The size of 15a is set to such a size that the circular bearing 16 can circularly move with the deviation amount e as a radius. The knife 14 can move in a proper position with respect to the stay 13 at a proper position.

Further, at the center of the motor M side of the runner 14, a boss 14 c is provided, and a bearing 17 rotates in the boss 14 c. The crank pin 3 a of the crank shaft 3 described above is inserted into the bearing 17, and is inserted into the bearing 17. It is fitted. The axis of crank pin 3a is indicated by G.

As a result, the rotation of the crankshaft 3 around the vehicle center of rotation F and the eccentricity e of the crankpin 3a due to the rotation of the crankshaft 3 around the center of rotation F causes the circular motion with the radius equal to the radius. Thus, the runner 14 is forced to move circularly with a radius e with respect to the stator 13. In other words, the axis F of the crankshaft 3 is disposed so as to be located at the center of the stator 13 and the axis F of the crankshaft 3 The crank pin 3a is eccentric with respect to F. Since it is located at the center of the runner 14 by force, it follows the circular movement of the crank pin 3a. The runner 14 moves circularly with respect to the stay 13 with the eccentricity e as the radius.

At this time, the crank pin 3a is rotated by the rotating force (the rotation is absorbed by the bearing 17), and thus the runner 14 revolves immediately. That is, while maintaining the parallel state, each part moves so as to draw a small circle with the eccentricity e as the radius.The movement at this time is the circular movement. It is smoothed through the function 16.

When the relative movement between the stator 13 and the runner 14, that is, the runner 14 circularly moves with respect to the stator 13, both forces 13 and 14 are applied. The ends of the shit are made to come close to each other. To prevent abrasion, force, and kinking due to this proximity, the bottom of the stay 13 should be made of a dissimilar metal bottom that conforms to the shape of the compression chamber 24 described below. 1 18 is also the runner 14 On the end face adjacent to the bottom plate 18, a chip seal 19 along the end face shape of the runner 14 is provided. Further, the end face of the stator 13 adjacent to the runner 14 is provided with a chip seal 20 along the end face shape of the stator 13. I'm nervous.

As shown in FIG. 6, a gas such as a cooling gas is introduced into the inside of the casing 4 as shown in FIG. 6, and the suction provided in the stator 13 is formed on the peripheral wall of the casing 4. This gas is introduced into the compression chamber 24 described below from the port 13a (see Fig. 5), and the suction port 21 is compressed in the compression chamber 24 and installed in the stay 13 Discharged outlets 1 3b Discharge ports 22 for discharging the compressed gas guided into the casing 4 out of the casing 4 are provided respectively. I'm nervous.

The stator 13 is stored slightly forward of the casing 4 (to the right in FIG. 1), and is thereby stored in the stator 13. A space 4a is formed between the rear surface and the casing 4 so that the discharge port 22 and the circumference of the stator 13 communicate with this space. Each of the suction ports 21 is provided so as to communicate with a space 4b provided between the wall and the casing 4. Then, the suction port 21 and the gas led into the space 4b of the casing 4 are supplied to the suction port 21 provided on the peripheral wall of the stay 13. The 13a force is introduced into the interior of the stay and compressed, and the compressed gas is discharged from the outlet 13b provided on the rear wall of the stator 13. It is guided to the space 4 a in the casing 4, and is discharged from the discharge port 22. It has been done.

As described later, the discharge port 22 has a capacity of a sealed compression space formed between the arc vane 25 and the inner wall of the compression chamber 24 having a volume of zero. In addition to this, the discharge port 22 is provided with a leaf spring 23 radially extending with its center pressed against a stay 13 (FIG. 2). (See Ref.). The leaf spring 23 acts as a discharge valve, thereby reducing the volume of the compression space and reducing the pressure of the gas inside the compression space. When the pressure reaches a predetermined pressure, that is, a pressure that overcomes the elastic force of the leaf spring 23, the discharge port 22 is opened.

FIG. 2 shows details of the stay 13 and FIG. 3, details of the runner 14 are shown in FIG. 3, and FIG. 4 shows a state where the stay 13 and the runner 14 are combined. Show. In this embodiment, the thickness t of the peripheral wall 13C of the stay is set to 4 mm (t = 4 Dim), and the eccentricity e is set to 5.5 mm (e = 5.5 mm). The inner diameter R l of the casing 4 is set to 67 mm (R l = 67 mm), and the number of compression chambers is set to three, which is the most efficient. .

Inside the cylindrical stator 13, a total of three compression chambers 24 are provided, and each of the compression chambers 24 is arranged as follows. It is configured . First, an inner reference circle having a radius R 2 (R 2 = 19.7 mm) and a radius R 3 (R 3 = R 3 = R 3 = R 3 (R 3 = R 3) Draw a concentric outer reference circle (10.97 + 5.5 + 4 = 20.47 mm). These two reference circles and 120 cross each other through the center of these reference circles. Find each of the three intersections A and B with the line drawn at intervals of.

Then, with each of these intersections A as a center, a half-arc having a radius R 4 (R 4 = 2 mm) of half the thickness t, and with each of the intersections B as a center, a displacement e and Draw a semicircular arc of radius R5 (R5 = 5.5 + 2 = 7.5 mm) to which half the wall thickness t has been added in the opposite direction as a continuous curve. Furthermore, an arc having a radius R 6 (R 6 = 7.5 x 2 + 2 = 17 mni) obtained by adding a length twice as long as the radius R 5 and a half of the wall thickness t is formed at each intersection A. The center is drawn concentrically with the arc of the radius R 4, and one end of the arc is continuous with the arc of the radius R 5, and the other end is continuous with the adjacent arc of the radius R 4. The contours of the three compression chambers 24 are obtained by connecting them in a curved shape.

Each of the compression chambers 24 has four arcs smoothly connected to each other in a continuous curved shape, namely, an arc having a radius R5 and an arc having a radius R6, and these arcs. It is defined by the inner walls of two arcs of radius R4 that are continuous with the arc. Then, the portion of the arc having the radius R 4 forms a tip protrusion 27 (FIG. 4) directed inward.

A circle with a radius R7 (R7 = 17 + 4 = 21 mm) is drawn concentrically with the circle with the radius R6 and centered on the intersection A with the thickness t added to the radius R6. Each of the compression chambers 24 is formed by a plurality of arcs smoothly and smoothly connected to this circle in a continuous curved shape. The outer wall of the peripheral wall 13 C that constitutes is defined. On the other hand, the runner 14 is provided with three arc-shaped plate-like vanes 25, and each of the arc-shaped vanes 25 is as follows. It is configured for

First, as in the case of the above-mentioned star 13, the radius R 1G (R 10 =

R 2 = 10.97 min) and 120 through each other through the center of this reference circle. 3 intersections with lines drawn at intervals

C ¾ · Ask.

A radius R ii (. RU = R 5 = 5.5 + 2 = 7.5 ram) obtained by adding half of the thickness t to the displacement e around the intersection C ) And an arc of a radius R12 (R12 = 7, 5 + 4 = 11.5 mm) obtained by adding the thickness t to the radius R11, and radii that are adjacent to each other R 11 and an arc having a radius R 12 are connected in a continuous curved line, and the above-mentioned 120 is formed. The three protruding ends from the line drawn at the interval of are connected by an arc with a radius R13 (R13 = 2 mm) that is half the thickness t. 25 contours are required.

Each of the arc vanes 25 is composed of three arcs smoothly and continuously connected to each other in a curved shape, namely, an arc having a radius R11 and an arc having a radius R12. The arc is bounded by the peripheral wall of an arc of radius R13 connecting the ends of these arcs. More specifically, the inner diameter R ll and the thickness t are 210. The three semi-cylindrical members having a predetermined width at an angle of 120 ° are arranged at an interval of 120 ° from each other, and the distal end portion and the connecting portion are formed in an arc shape. And 3 An individual arc base 25 is formed.

Then, as shown in FIG. 4, each arc vane 25 of the runner 14 is placed in each compression chamber 24 of the stay 13, and the curved vane 25 has a curved shape. The center of the stay 13 and the center of the runner 14 are displaced from the center of the stay 13 along with the curvature of the peripheral wall 13 c of the stay 13. By disposing it only by the amount e (= 5.5 mm), the positional relationship between the two is set.

At this time, the stay 13 and the runner 14 are in contact with each other at 4 to 5 places along the entire length in the width direction. The volume partitioned by the part will change continuously.

In the case of this embodiment, if the stay 13 is fixed in the casing 4 and the runner 14 is housed inside the stay 13, In addition, the runner 14 is irremovably held by the fixing plate 15. Then, the center of the stay 13 and the axis thereof are made to coincide with each other, and the crank pin 4a is provided at a position displaced only by the displacement amount e. By inserting the crank shaft 3 into the cylindrical projection 14 a at the center of the runner 14, the crank shaft 3 a is fitted. Thus, both 13 and 14 can be accurately set in a predetermined positional relationship.

Next, the principle of the above-mentioned compressor, that is, the principle of compressing and discharging gas such as refrigerant gas by means of the stay 13 and the runner 14 is shown in FIG. A or No Refer to the operation cycle diagram shown in Fig. 5D. Refer to and explain.

First, FIG. 5A shows a state in which gas is being sucked into one compression chamber 24, and at this time, there is no gas in this compression chamber 24. The suction port 21 provided in the casing 4 and the gas introduced into the casing 4 are sucked into the interior of the casing by the suction port 13a. (The gas inhaled at this time is indicated in a number of ways, and so on.)

In this state, when the crank shaft rotates three times and the runner moves in a circular direction with respect to the runner, the compression starts as shown in Fig. 5B. Position (inhalation end position '). In other words, at this time, a closed space is formed by the inner wall of the compression chamber 24 and the arc vane 25 of the runner 14.

Further, when the crankshaft is further rotated by three forces and the runner is rotated by four forces, as shown in FIG. 5C. Then, the volume of the closed space is gradually reduced, and the gas sealed in this volume is compressed. Immediately, the runner 14 is moved in a circular motion with respect to the stay 13, so that the components constituting the runner 14 change the displacement e. As a result, a circular motion as a radius is performed, and as a result, the volume of the enclosed space is gradually reduced.

The pressure of the gas sealed by the compression increases, and when the pressure becomes larger than the elastic force of the leaf spring 23, the leaf spring 23 is displaced and discharged. The outlet 1 3b opens, and this force and pressure

Four The compressed gas comes out and 'discharge starts as shown in Fig. 5D. Then, when this volume becomes zero, the compression work in the compression chamber 24 is completed.

This compression work is also performed in the other two compression chambers 24 in the same way with a phase shift of 12 °, and the rotation of the crank shaft 3 is performed. As a result, this compression work is continued. That is, in FIG. 4, one compression chamber 24 (A) indicates a compression start position, another compression chamber 24 (B) indicates a suction position, and another compression chamber 24 (C). ) Takes the discharge position from compression respectively. '

In the case of the above embodiment, it is possible to obtain a discharge amount that is several percent higher per rotation than a scroll type compressor of the same size.

Although three compression chambers 24 are provided in the above embodiment, one or two compression chambers 24 may be provided. It can also be used as a pump.

FIG. 7 to FIG. 13 show a second embodiment of the present invention. This embodiment has the same principle as the first embodiment described above, but has a better effect.

FIG. 7 shows a diagram corresponding to FIG. 4, and FIG. 8 shows a diagram corresponding to FIG. 5, respectively. The same parts as those in the first embodiment described above are denoted by the same reference numerals, and description thereof will be omitted.

The main difference between the second embodiment and the first embodiment is that Fig. 7 As clearly apparent from the above, the thickness of the arc vane 25 of the runner 14 is gradually increasing from its radial end toward the center. . The basic design of the arc vane 25 is the same as that described with reference to FIG. 3, but in the case of the second embodiment, the arc vane 25 shown in FIG. Based on the above, the thickness is increased toward the center so that the shape as shown in FIG. 9 is obtained. By designing the arc vane 25 in this way, the central portion where the arc vanes 25 gather is thickened as a whole. A large circular hole 30 can be formed in the portion as shown in FIG. The large circular hole 30 is a hole into which the crank pin 3a is inserted as shown in FIG. A small hole 31 can be formed on the bottom wall of the circular hole 30 for the purpose described below. Incidentally, in FIGS. 9 and 1, 31 is a hole for lubricating oil.

In the second embodiment, the stay 13 is configured as shown in FIG. 7, FIG. 11 and FIG. The design of Stay 13 can be done as shown in Figure 13. That is, after the shape of the runner 14 is determined as described above, the runner 14 is separated from the outer shape of the runner 14 by a width corresponding to the amount of eccentricity e. Define the inner surface of the By defining the shape of the stator 13 in this way, it is obvious that the peripheral wall 13c of the stator 13 is a natural force. As shown in (1), the thickness becomes non-uniform, and the thickness gradually increases outward from the front part of the projection 27. In addition, the contrast force between Fig. 2 and Fig. 11 There is no fundamental change in the position of the inlet 13a and outlet 13b.

As shown in FIG. 7, a runner 14 having a configuration as shown in FIG. 9 is inserted eccentrically into the interior of the stage 13 constructed as described above as shown in FIG. Thus, the compression chamber 24 is formed in the same manner as in the first embodiment. Thus, the configuration shown in FIG. 8 is obtained. In FIG. 8, a crankshaft 3 having an axis A has a crankpin 3a which is eccentric by only e, and this crankpin 3 a is inserted into the large circular hole 30 via the bearing 17. 'On the surface of the circular flange 14a of the runner 14, an annular thrust receiver 32 is in contact with the slide itself. In FIG. 8, 3b is a counterweight of crankshaft 3.

In the compressor of the present invention, if the axial dimension of the runner 14 is made longer than a certain degree, the circular flange 14a of the runner is formed. The balance between the axial thrust due to the compressed fluid pressure acting on the arc and the radial force due to the compressed fluid pressure acting on the arc vane 25 is broken, and the runner A couple is generated between the arc vane 25 of FIG. 14 and the crank pin 3 a, and as a result, the runner 14 is opposed to the axis of the compressor by force. It will rotate from a force that does not tilt. This will result in unnecessary friction between the opposite surfaces of the stay 13 and the runner 14 and will cause damage.

According to the second embodiment, such a problem is solved. Immediately Since the arc vane 25 of the runner is thicker toward the base, the center of the runner has a relatively large diameter for the crank pin 3a. A long circular hole 30 can be formed. By inserting the long and relatively large diameter crank pin 3a into this circular hole, the runner's arc base is formed by the compression and compression. Since the force that reaches the pin 25 is received by the crank pin 3a, no couple occurs, and therefore, the runner 14 operates smoothly. . In addition, since the axial dimension of the runner can be increased within the range of the strength of the crank pin 3a, the discharge amount can be increased. And are possible.

Also, into the circular hole 3 の at the center of the runner, small holes 31, and lubricating oil contained in the compressed gas (in the case of a hermetic refrigerant compressor) must be supplied. The lubrication of the crank pin portion can be performed satisfactorily.

In the state shown in FIG. 7, the force received by the runner 14 due to the compression pressure in the lower compression chamber 24 is the same as that of the runner 14 and the crank pin. The contact is received at the contact points P and Q between the runner 14 and the stator 13 in the same figure via the pin 3a. When the surfaces of the stator 13 and the runner 14 are treated by tuframing (surface hardening and abrasion treatment), the runners 14 at the contact points P and Q It can be slid with the help of lubricating oil while making direct contact with the stay 13. The contact points P and Q are the places where the fluid leaks most easily. However, since these parts are in sliding contact, the sealability is good. Also , Since the curved part of the large bay on the surface of the stay and the runner has a large radius of curvature or a radius of curvature close to each other, the vicinity of the approach point is relatively parallel. The sealability is good with the help of lubricating oil.

The compressor of the present invention, except for the crankshaft, can be used as an aluminum cast product, and requires the minimum necessary mechanical processing. Is possible.

FIG. 14 is a sectional view taken along the axis of a third embodiment of the compressor according to the present invention. In the figure, the compressor is generally indicated by reference numeral 1A, and the compressor 1A has a motor M as a rotary drive source. A rotary drive mechanism is provided. The drive shaft 43 is supported by a bearing 44 of the motor M, and is rotatable around an axis F. The compressor body 42 integrally has a cylindrical casing 4 concentric with the drive shaft 43. The drive shaft 43 extends to near the entrance of the casing 4.

An outer runner 13 is provided inside the casing 4 for rotation. The outer runner 13 corresponds to the stay 13 shown in FIG. 4 and constitutes an outer relative rotating member. The outer runner 13 has a disk portion 52 in the radial direction, and a cylindrical protrusion 51 is provided on one side in the axial direction of the outer runner 13. The protrusion 51 is connected to the outside of the drive shaft 43 by a key 50. The cylindrical projection 51 is rotatably supported by a bearing 49 inside the compressor body 42. The bearing 4 4

9 A bearing 48 is provided between the bearing 49 and the bearing 49. In a disk portion 52 of the outer runner 13, a partial cylindrical peripheral wall 13 c to be described later is formed physically on the opposite side of the cylindrical protrusion 51. .

Inside the outer runner 13, an inner runner 14 as an inner relative rotating member is provided. The inner runner 14 extends in the axial direction from the disk portion 14a and the disk portion 14a to the inside of the outer runner 13 The wall part 65 and the boss part 57 are integrally provided. Further, a cylindrical portion 59 is integrally formed on the disk portion 14a on the side opposite to the wall portion 65 so as to protrude therefrom.

A fixed shaft 6 ◦ is fixed to the end plate 4 a of the casing 4. The fixed shaft 60 has a flange 60a. The flange 60a is in contact with the inner surface of the end plate 4a, and is screwed into the outer end of the fixed shaft 60. The fixing member 60 is fixed in an immovable state by the set 62. The axis G of the fixed shaft 60 is eccentric with respect to the axis F of the drive shaft 3 by an eccentric amount e. The fixed shaft 60 is inserted into a hole in the boss portion 57 of the inner runner 14 at the tip portion 60 b of the inner runner 14, and the fixed shaft 60 is inserted between the boss portion 57 and the tip portion 60 b. Bearings 66 are interposed. A thrust receiving disk part 58 is interposed between the hole of the boss part 57 and the end face of the fixed shaft tip part 60b. An axial passage 60 c is formed inside the base of the fixed shaft 60, and a plurality of branch passages 60 d are provided near the tip thereof. The space between the partial cylindrical peripheral wall 13 c of the outer runner 13 and the wall portion 25 of the inner runner 14 serves as a compression chamber 64 described below. In addition, the outer runner 13 is formed with a suction port 13a which communicates with the inside of the compression chamber 24. Sucking mouth

In order to send the fluid to be compressed to 13a, a suction port 21 is formed in the casing 4.

On the other hand, the disk portion 14a of the inner runner 14 has a discharge port for discharging the compressed fluid compressed in the compression chamber 64.

All outlets 14b in which the number of 14b is equal to the number of compression chambers 64 are normally closed by leaf springs 63 that function as discharge valves. Sick. The leaf spring 63 has a shape in which a plurality of spring pieces integrally project radially inward from the ring-shaped main body, and each spring piece closes each discharge port 14b. . The ring-shaped main body of the leaf spring 63 is held via a screw 68 by an annular leaf spring retainer 69 provided inside the cylindrical portion 59. It is. The leaf spring retainer 69 prevents the escape from the inside of the cylindrical portion 59 by the stopping member 70, and also closes the leaf spring 63 to the discharge port 14b. It is pressed into the disk section 14a. Each discharge port 14 b is opened by bending the leaf spring 63 to the left in FIG. 14 by the pressure in the compression chamber 64, and the compressed fluid flows through each discharge port. It is discharged through a passage 60c via a branch passage 60d located at a position facing 14b.

The details of the outer runner 13 are shown in Figure 15 and the inner runner FIG. 16 shows details of 14 and FIG. 17 shows a state in which the outer runner 13 and the inner runner 14 are combined. In this embodiment, the number of compression chambers is set to three, which is the most efficient, respectively.

That is, a total of three compression chambers 64 are provided inside the peripheral wall 13 c of the outer runner 13. Since each of the compression chambers 64 is configured in the same manner as described above with reference to FIG. 2, the description thereof will be omitted.

On the other hand, as shown in FIG. 16, the wall portion 65 of the inner runner 14 is formed as three arc plate-shaped 'arc vanes 65'. However, each of the arc vanes 65 is also configured in the same manner as the arc vane 25 described above with reference to FIG. The explanation is omitted here.

As shown in FIG. 17, each arc vane 65 of the inner runner 14 is located in each compression chamber 64 of the outer runner 13, and at the same time, By arranging the center of the side runner 13 and the center of the inner runner 14 with a deviation amount e, the positional relationship between the two runners 13 and 14 is set. .

At this time, the outer runner 13 and the inner runner 14 are in close proximity to each other at four to five locations over the entire length in the width direction. The volume partitioned by the proximity will change continuously.

Fig. 18 shows the planar shape of the compressor configured as described above. Next, the principle of the compressor described above, that is, the outer runner 13 which is an outer relative rotating member, and the inner runner 14 which is an inner relative rotating member, are used. The principle of compressing and discharging gas such as refrigerant gas will be described with reference to the working cycle diagram shown in FIG. 19A or FIG. 19D.

First, FIG. 19A shows a state in which gas is being sucked into one compression chamber 64, and at this time, the inside of the compression chamber 64 is The suction port 21 provided in the casing 4 and the gas guided into the casing 4 is sucked into the interior through the suction port 13a '( The gas that is inhaled at this time is indicated by a number of points, which is the same in the following.)

In this state, when the outer runner 13 rotates in the direction of the arrow K with the rotation of the rotary drive shaft 43 by the motor M, the eccentricity of both runners causes the arrow to move. Pressing the arc vane 65 with the peripheral wall 13 of the K-applied part in contact with its inside in the counterclockwise direction in FIG. The runner 14 starts rotating relative to the outer runner 13 in the counterclockwise direction, and immediately reaches the compression start position (suction end position) shown in FIG. 19B. At this time, a closed space is formed by the inner wall of the compression chamber 64 and the arc vane 65 of the inner runner 14.

Then, when the outer runner 13 rotates further and the inner runner 14 rotates, the outer runner 13 rotates relative to the outer runner 13. As shown in the figure, the volume of the sealed space 64 gradually decreases, and the gas sealed in this volume becomes smaller. Is compressed. Immediately, the inner runner 14 relatively rotates with respect to the outer runner 13, so that the volume of the sealed space 64 is gradually increased. You can make it smaller.

The pressure of the gas sealed by this compression increases, and when this pressure becomes greater than the elastic force of the leaf spring 63, the leaf spring 63 3 is displaced and discharged. Outlet 14b is opened and exhalation begins. Then, when this volume becomes zero, the compression work in the compression chamber 64 is completed.

This compression work is similarly performed in the other two compression chambers 64 with the phase shifted by 120 °, and is sequentially performed as the outer runner 13 rotates. This compression work will continue. In other words, in FIG. 17, one compression chamber 64 (A) indicates the compression start position, the other compression chamber 64 (B) indicates the suction position, and the other compression chamber 64 (A) indicates the compression position. C) takes the discharge position from the compression respectively. The rotation of the outer runner 13 is always transmitted to the inner runner 14 by the compression pressure.

In the case of the third embodiment as well, it is possible to obtain a discharge amount that is several orders of magnitude higher per rotation than that of a scroll-type compressor of the same size. it can .

In the third embodiment, three compression chambers 64 are provided, and one or two compression chambers may be provided. . This compressor can also be used as a pump.

FIG. 20 shows a fourth embodiment of the present invention. This embodiment is The principle is the same as that of the second embodiment (FIG. 7) described above. FIG. 20 shows a diagram corresponding to FIG. The same parts as those in the third embodiment described above are denoted by the same reference numerals, and description thereof will be omitted. The effect of modifying the embodiment of FIG. 17 as shown in FIG. 20 is the same as the effect of modifying the embodiment of FIG. 4 as shown in FIG.

FIG. 21A or FIG. 21D is a diagram showing an operation cycle of the fourth embodiment shown in FIG. In the state shown in FIG. 21A, a closed space 64 is formed between the outer runner 13 and the inner runner 14 and compression is about to be started. In the state of FIG. 21B, the compression of the fluid in the closed space 64 is further advanced, and when the state of FIG. 21C is reached, the closed space 64 becomes extremely small. The discharge is about to end, and in the state of FIG. 21D, the volume of the sealed space 64 becomes zero, and the discharge is completed.

In the third and fourth embodiments, even though the outer runner and the inner runner are eccentric, each runner itself has a good rotational balance. The vibration of the press can theoretically be reduced to zero.

As described above, according to the present invention described in the embodiment, since the driving torque fluctuation is small and gradual, the driving is performed smoothly. If the driving noise is very low, it is possible to operate at high speed without force or power, and high efficiency is obtained because there is little energy loss due to force and friction. In addition, the outer relative rotation member and the inner relative rotation member are continuous. Since it can be formed by curved arcs, it is possible to easily perform high-precision machining by keeping the center of each component arc accurate. Effectiveness

Industrial applicability

The compressor of the present invention is suitable for compressing a gas such as a refrigerant in a refrigerator, but can also be used as a pump.

Claims

The scope of the claims

1. An outer relative rotation member having a first axis, a second axis parallel and eccentric to the first axis, and an inner side of the outer relative rotation member. Relative to the inner relative rotation member and the outer relative rotation member and the inner relative rotation member while maintaining a distance at which the first and second axes are eccentric. And a means for rotatably driving the relative rotating members relative to each other, wherein the outer relative rotating member has at least one peripheral wall having a partial cylindrical shape. A distal end protruding inward from the peripheral wall so as to approach the first axis, and the inner relative rotating member has a second axial force and an outward force. Has at least one arc-shaped plate-shaped arc vane extending toward the The closed space is formed inside the peripheral wall, and the volume of the closed space changes with the relative rotation of the two relative rotating members. And a suction port is provided in a part of the peripheral wall, respectively.

2. The outer relative rotation member is a stator that is non-rotatably provided in the casing, and the inner relative rotation member moves circularly with respect to the stay. 2. The compressor according to claim 1, wherein said rotary drive means is connected to said runner in a circular drive relationship.

3. A crankshaft is provided, which is rotatably driven by the rotary drive means, and the crankshaft rotates about the first axis. A crankpin located at the center of the second axis, and the runner is supported by the crankpin. Compressor described in range 2

4. The compressor according to claim 2, wherein said discharge port is formed in a stator.

5. The outer relative rotation member is an outer runner provided in the casing in a rotating manner around the first axis, and the rotation driving means is provided on the outer runner. An inner rotary member connected in a rotational drive relationship, wherein the inner relative rotating member is rotated about the second axis together with the rotation of the outer runner. The compressor according to claim 1, wherein the compressor is a carrier.

6. The compressor according to claim 5, wherein the inner runner is rotatably supported by the fixed shaft having the second axis.

7. The compressor according to claim 6, wherein said discharge port is formed in an inner runner.

8. The compressor according to claim 7, wherein a discharge passage is provided in the fixed shaft following the discharge port.

9. The center of the tip protrusion is located on an inner virtual reference circle centered on the first axis of the outer relative rotation member, and the inner surface of the partial cylindrical peripheral wall is the inner surface of the tip protrusion. Smoothly A first concave semicircle of a certain radius centered on a point on the outer virtual reference circle larger than the inner virtual reference circle and the peripheral wall having a radius of the concave semicircle. A radius of curvature of a value obtained by adding one-half of the thickness of the second protrusion to the second concave semi-circular arc centered on the center of the tip protrusion. The second concave semicircular arc is formed by smoothly connecting a second distal end similar to the distal end to the opposite end of the second concave semicircular arc to the first concave semicircular arc. The compressor of claim 1.

10. The inner end of the arc vane of the inner relative rotation member is on the second axis, and the outer end of the arc vane is on a radius extending from the second axis. A compressor according to claim 1.

11. The compressor according to claim 1, wherein the arc vane is curved substantially along a concave curve of the inner surface of the partial cylindrical peripheral wall.

12. The arc vane of the inner relative rotation member is formed so as to gradually increase in thickness toward the base close to the second axis. The compressor described in 1.

13 3. The inner contour of the peripheral wall and the tip projection of the outer relative rotating member and the outer contour of the arc vane of the inner relative rotating member define both relative rotating members as the first and second axes. 2. The compressor according to claim 1, wherein the compressor is configured so as to be separated by a distance corresponding to the amount of eccentricity when the centers are aligned.