CN1118182A - rotary compressor - Google Patents

Abstract

A rotary compressor includes a cylinder (5) having a cylinder chamber (51) with a suction hole (52) and a discharge hole (53), and an eccentric shaft portion (31) fitted on a drive shaft (3). ) and mounted on the rotor (7) in the cylinder chamber (51), and divide the interior of the cylinder chamber (51) into a low-pressure chamber (X) communicating with the suction hole (52) and the discharge hole ( 53) The vane (9) of the high-pressure chamber (Y) communicated, the above-mentioned suction hole (52) is formed so that the centerline (a ) is inclined toward the vane (9) side with respect to a normal line (c) perpendicular to a tangent line (b) of a virtual intersection point of the center line (a) on the inner peripheral surface of the cylinder chamber (51). According to this structure, the flow resistance when the gaseous fluid is sucked in from the suction hole (52) and the cylinder chamber (51) can be reduced, and the pressure loss of the sucked gaseous fluid in the low-pressure chamber (X) can be reduced.

Description

rotary compressor

technical field

The present invention relates to rotary compressors mainly used in refrigeration installations.

Background technique

As a conventional rotary compressor, there is, for example, the one described in Japanese Unexamined Application Publication No. 63-54882. As shown in FIG. The rotor C on the eccentric shaft part S of the above-mentioned cylinder A is provided with a front end cover (not shown) on one side of the axial direction of the above-mentioned cylinder A, and a rear end cover (not shown) is provided on the other side of the axial direction At the same time, the suction hole D and the discharge hole E opening to the above-mentioned cylinder chamber A1 are formed at regular intervals in the circumferential direction, and the blade holding groove F extending in the radial direction is provided between the suction hole D and the discharge hole E. The holding groove F is provided with a vane G that can move forward and backward. By keeping the tip of the vane G in constant contact with the outer peripheral surface of the rotor C, the interior of the cylinder chamber A1 is divided into a low pressure that communicates with the suction hole D. Chamber X, and the high-pressure chamber Y communicating with the above-mentioned discharge hole E. In addition, the above-mentioned suction hole D is located near the vane G of the cylinder A, and in the radial direction toward the center of the above-mentioned cylinder chamber A1, in other words, in the center line of the above-mentioned suction hole D and the inside of the cylinder chamber A1. The tangent line of the peripheral surface is formed in a direction perpendicular to the tangent line at the point where the inner peripheral surface intersects with the central line of the suction hole D. In addition, the above-mentioned rotor C is composed of two inner and outer rotor members.

According to the above structure, there is a problem that since the above-mentioned suction hole D is formed in the position of the air cylinder A close to the vane G and in the radial direction toward the center of the above-mentioned cylinder chamber A1, when the suction hole D is formed from the above-mentioned When the hole D sucks gaseous fluid into the low-pressure chamber X of the cylinder chamber A1, as shown by the arrow m in FIG. It is introduced into the side of the low-pressure chamber X opposite to the vane in a nearly vertical state, so the flow resistance of the sucked gaseous fluid sucked into the low-pressure chamber X from the suction hole D is increased, resulting in a loss of suction pressure of the low-pressure chamber X. increase.

disclosure of the invention

It is an object of the present invention to provide a rotary compressor capable of reducing flow resistance when sucking gaseous fluid from a suction hole into a low-pressure chamber of a cylinder chamber and reducing suction pressure loss in the low-pressure chamber.

In order to achieve the above object, the rotary compressor of the present invention includes a cylinder having a cylinder chamber having a suction hole and a discharge hole, and a rotor fitted on the eccentric shaft portion of the drive shaft and installed in the cylinder chamber, and The vane that partitions the interior of the cylinder chamber into a low-pressure chamber communicating with the suction hole and a high-pressure chamber communicating with the discharge hole, and the suction hole is formed so that the side of the suction hole that opens to the cylinder chamber The centerline is inclined toward the vane side with respect to a normal line perpendicular to a tangent to a virtual intersection point of the centerline on the inner peripheral surface of the cylinder chamber.

According to the above configuration, since the suction hole is formed such that the center line of the suction hole at least on the side that opens to the cylinder chamber is tangent to the imaginary intersection point with the center line on the inner peripheral surface of the cylinder chamber The vertical normal line is inclined toward the vane side, so when the gaseous fluid is sucked from the suction hole to the low-pressure chamber of the cylinder chamber, the sucked gaseous fluid will not come into contact with the outer peripheral surface of the above-mentioned rotor perpendicularly, but in the same manner as The tangents of the outer peripheral surfaces collide at an angle close to each other, and the inhaled gaseous fluid after the collision is reflected toward the rotation direction of the above-mentioned drive shaft, so that the inhaled gaseous fluid can smoothly flow into the above-mentioned low-pressure chamber, and its flow resistance can be reduced. The pressure loss of the inhaled gaseous fluid in the low pressure chamber.

In one embodiment of the present invention, the centerline of the side of the suction hole connected to the suction pipe faces toward the center of the cylinder chamber. Therefore, when the suction pipe or the introduction pipe connected to the suction pipe is press-fitted and fixed to the above-mentioned suction hole, the suction pipe or the like can be connected toward the center of the above-mentioned cylinder, so that it is possible to prevent the suction pipe or the introduction pipe from moving toward the center of the cylinder. Problems that arise when press-fitting in substantially the same direction as the centerline of the opening side, that is, if press-fitting is performed along the direction of the centerline of the opening side, the cylinder will be rotated As a result, rotational torque is generated, which causes parts to be twisted, and problems such as misalignment of assembly gaps are prone to occur. In addition, it is also possible to solve the problem that, in an ordinary rotary compressor, the arrangement position of the above-mentioned vane is close to the above-mentioned suction hole, and the front end cover and the rear end cover which are closing members are combined with the cylinder by screws. In this case, the space for tightening the screws cannot be ensured between the vane and the suction hole. Therefore, the gap between the end surface of the cylinder and the end surfaces of the closure members such as the front end cover and the rear end cover arranged along the axial direction of the cylinder The surface pressure is reduced, resulting in the problem of leakage between the various end faces. In addition, when the suction pipe is supported by the connection pipe, if the center line of the entire suction hole is inclined toward the vane side in a direction close to the tangent line, that is, with respect to a normal line perpendicular to the tangent line, then the connection pipe will also If it is to be fixed to the above-mentioned housing in the direction of the center line, the shape of the connecting pipe needs to be changed into a special shape, and the parts used in the past cannot be used, so that the common use of parts cannot be realized, and the welding work is difficult. conduct. However, the above-mentioned problems are overcome in this embodiment.

Therefore, the flow resistance of the gaseous fluid can be reduced, the pressure loss in the low-pressure chamber can be reduced, and at the same time, the distortion of the parts and the misalignment of the assembly gap can be prevented, and the gap between the disposition position of the above-mentioned vane and the inlet side of the above-mentioned suction hole can be ensured. space, so that screw reinforcement can be realized, so that leakage from the end surface of the above-mentioned closing member can be prevented, and since the connecting pipe connected to the above-mentioned suction pipe can be connected toward the center of the above-mentioned cylinder, it can be used in the past. The connecting pipe is universal, and the welding work is also simple and easy.

In another embodiment, a suction passage communicating with the suction pipe is provided on a closing member attached to one side of the cylinder in the axial direction and used to close the one side of the cylinder in the axial direction, and the top end side of the suction passage forms a It has a shape inclined toward the above-mentioned cylinder and is connected to the above-mentioned suction hole.

According to the above configuration, even if the cylinder and the rotor have a flat shape with a short length in the axial direction, flow resistance can be reduced and suction can be performed from the closing member. That is, when making the above-mentioned rotor and the above-mentioned cylinder chamber into a flat shape with a large inner diameter to reduce the dimension in the axial direction to achieve miniaturization, or shorten the length in the axial direction by using a plurality of cylinders In the case of one cylinder, the diameter of the suction pipe connected to the cylinder becomes smaller with the flattening of the cylinder, and a sufficient suction hole size cannot be obtained. If the suction passage is provided on the member, the necessary suction hole size can be ensured, and since the top side of the suction passage is inclined to the cylinder, and it is connected to the normal direction perpendicular to the above-mentioned tangent to the inner peripheral surface of the above-mentioned cylinder chamber. The suction hole is inclined on the side of the vane, so that a necessary amount of gaseous fluid corresponding to the volume of the cylinder chamber can be introduced into the low-pressure chamber in the cylinder chamber from the suction pipe through the suction passage and the suction hole while reducing flow resistance. In this way, the pressure loss in the low-pressure chamber can be reduced.

In addition, in yet another embodiment, the center line of the inlet side of the suction passage formed on the above-mentioned closing member, which communicates with the suction pipe, is toward the center of the cylinder chamber, and the center of the side of the suction passage connected to the suction hole is toward the center of the cylinder chamber. The line is inclined in the same direction as the centerline of the side of the suction hole opening to the cylinder chamber.

In this case, the suction pipe may be connected toward the center of the cylinder. Therefore, a necessary amount of gaseous fluid corresponding to the volume of the cylinder chamber can be introduced from the suction pipe through the suction passage and the suction hole into the low-pressure chamber in the cylinder chamber with reduced flow resistance, thereby reducing the pressure in the low-pressure chamber. At the same time, it can prevent the distortion of the parts and the misalignment of the assembly gap, and can also ensure the space for screw fixing between the arrangement position of the above-mentioned vane and the inlet side of the above-mentioned suction hole, thereby preventing leakage.

In another embodiment, the blades are protrudingly coupled to the outer peripheral portion of the rotor, and a rocking bush is rockably held on the cylinder, and the rocking bush has a protruding tip side capable of receiving the blades in a forward and backward manner. A receiving groove; on the outer peripheral surface of the above-mentioned rotor opposite to the above-mentioned suction hole opening to the above-mentioned cylinder chamber, a guide groove that can guide the suction gaseous fluid introduced from the suction hole to the above-mentioned low-pressure chamber is recessed inward.

In this case, the space between the outlet of the suction hole and the outer peripheral surface of the rotor can be enlarged, and the space can reduce the suction resistance when gaseous fluid is sucked from the suction hole to the cylinder chamber, and can also be used by the guide groove. Inhaled gaseous fluid is introduced into the low-pressure chamber side more smoothly. Therefore, the flow resistance can be further reduced, and the pressure loss of the sucked gaseous fluid in the low-pressure chamber X can be further reduced.

Brief description of the drawings

Fig. 1 is a transverse sectional view of main parts of a first embodiment of a rotary compressor according to the present invention.

Fig. 2 is an enlarged sectional view along line 2-2 in Fig. 1 .

Fig. 3 is a transverse sectional view showing a second embodiment.

Fig. 4 is a transverse sectional view showing a third embodiment.

Fig. 5 is an enlarged sectional view along line 5-5 in Fig. 4 .

Fig. 6 is a sectional view showing a fourth embodiment.

Fig. 7 is a partial plan view of the fifth embodiment.

Fig. 8 is a longitudinal cross-sectional view showing a part of the overall structure of the rotary compressor.

Fig. 9 is a sectional view showing an example of the prior art.

The best form for carrying out the invention

The first embodiment is now described in conjunction with the accompanying drawings. In the rotary compressor shown in FIG. 8 , a motor 2 is provided above the inside of the airtight casing 1 , and a compression element driven by a drive shaft 3 extending from the motor 2 is arranged on the lower side of the motor 2 . 4. The compression element 4 includes a cylinder 5 having a cylinder chamber 51 inside, and closing members 6, 6 composed of a front end cover and a rear end cover that are closed from both sides in the axial direction of the cylinder 5, and are fitted in the above-mentioned The rotor 7 is mounted on the eccentric shaft portion 31 of the drive shaft 3 and installed in the cylinder chamber 51 .

As shown clearly in Fig. 1 and Fig. 2, the suction pipe 8 inserted from the outside of the airtight casing 1 is connected to one end of the above-mentioned cylinder 5 via the introduction pipe 81, and the other end is formed to open to the above-mentioned cylinder chamber 51. The suction hole 52 of the above-mentioned casing 1 and the discharge hole 53 opening to the discharge space of the above-mentioned housing 1 are provided with a vane 9 between the above-mentioned suction hole 52 and the discharge hole 53, and the vane 9 separates the interior of the above-mentioned cylinder chamber 51 from the above-mentioned A low-pressure chamber X communicated with the suction hole 52 and a high-pressure chamber Y communicated with the above-mentioned discharge hole 53 .

In the rotary compressor of the first embodiment shown in FIG. 1 , the above-mentioned blades 9 are configured to be oscillating, thereby constituting an oscillating compressor. That is, the base end side of the vane 9 is buried in a part of the outer circumference of the rotor 7 so as to protrude outward in the radial direction, and on the cylinder chamber side in the radial direction of the cylinder 5, in the suction hole. Between 52 and the discharge hole 53, a cylindrical rocking bush 10 is held. The bush 10 has a receiving groove 10a capable of freely receiving the protruding tip side of the above-mentioned vane 9, and the protruding tip side of the above-mentioned vane 9 can move forward and backward. And can be rockably inserted into the receiving groove 10a of the rocking bush 10, therefore, the above-mentioned blade can be moved forward and backward relative to the receiving groove 10a of the above-mentioned bush 10 with the rotation of the above-mentioned drive shaft 3, and through the The bushing 10 oscillates the partition plate 9 relative to the cylinder 5, and at the same time, causes the rotor 7 to revolve in the cylinder chamber 51 instead of rotating on its own, and divides the inside of the cylinder chamber 51 from the suction hole by the blade 9. The low-pressure chamber X communicated with 52 and the high-pressure chamber Y communicated with the discharge hole 53.

In the case of constituting the above-mentioned oscillating compressor, since the above-mentioned vane 9 and the above-mentioned rotor 7 are integrated, it can be like a revolving compressor that keeps the protruding tip side of the above-mentioned vane 9 in constant contact with the outer peripheral surface of the above-mentioned roller 7. The high-pressure fluid in the high-pressure chamber Y is effectively prevented from leaking from the contact surface between the rotor 7 and the vane 9 to the low-pressure chamber X side, so that the compression efficiency can be improved. Furthermore, since no sliding occurs between the vane 9 and the outer peripheral surface of the rotor 7, the friction between the rotor 7 and the vane 9 is reduced, thereby reducing power loss.

In the above configuration, the suction hole 52 of the rotary compressor shown in FIGS. 1 and 2 is formed such that the center line a of the suction hole 52 at least on the side that opens to the cylinder chamber 51 faces the cylinder. The direction in which the inner peripheral surface of the chamber 51 approaches the tangent line b of the imaginary intersection point of the above-mentioned center line a is inclined. That is, the above-mentioned suction hole 52 is formed on the above-mentioned cylinder 5 so that if the center line of the above-mentioned suction hole 52 is a, the tangent line of the imaginary intersection point between the inner peripheral surface of the above-mentioned cylinder chamber 51 and the above-mentioned center line a is b, assuming that the straight line perpendicular to the tangent b, i.e. the normal line, is c, then the centerline of the suction hole 52 is inclined toward the blade 9 side with respect to the above-mentioned straight line c, that is, it is inclined toward the direction of the above-mentioned tangent b.

As mentioned above, when the above-mentioned suction hole 52 is formed on the above-mentioned cylinder 5, it is formed so that the center line a passing through the suction hole 52 faces toward the inner peripheral surface of the cylinder chamber 51 where the suction hole 52 is formed. The direction in which the tangent line b on the above-mentioned b is close is inclined, so when the gaseous fluid is sucked from the above-mentioned suction hole 52 to the low-pressure chamber X of the above-mentioned cylinder chamber 51, the sucked gaseous fluid will not collide perpendicularly with the outer peripheral surface of the above-mentioned rotor 7, but It collides with the outer peripheral surface at an angle close to the tangent of the outer peripheral surface, so that the inhaled gaseous fluid after the collision is reflected in the rotation direction of the drive shaft 3, so that the gaseous fluid can be smoothly discharged while reducing the flow resistance. The fluid is introduced into the low-pressure chamber X through the suction hole 52, so that the pressure loss in the low-pressure chamber X of sucking gaseous fluid can be reduced.

Example 2 will be described below. In the rotary compressor shown in FIG. 3 , the shape of the suction hole 52 formed in the cylinder 5 is changed so that the center line d of the side of the suction hole 52 connected to the suction pipe faces the center of the cylinder chamber 51. , and the centerline a of the side of the suction hole 52 that opens to the cylinder chamber 61 is inclined in a direction in which the tangent line b of the imaginary intersection point between the inner peripheral surface of the cylinder chamber 51 and the centerline a approaches, and the above-mentioned The suction holes 52 are formed in a curved shape on the same plane, so that the problems caused by the above-mentioned first embodiment described later can be eliminated.

That is to say, according to the above-mentioned first embodiment, when the above-mentioned suction pipe 8 is connected to the above-mentioned suction hole 52 via the above-mentioned introduction pipe 81, if the above-mentioned introduction pipe 81 is pressed and fixed in the direction of the above-mentioned center line a and If it is connected, although the effect of reducing the flow resistance in the cylinder chamber 51 and reducing the pressure loss can be obtained, since it is pressed in the direction of the above-mentioned center line a, the above-mentioned cylinder 5 will be rotated, thereby generating a turning torque. Therefore, problems such as twisting parts and misalignment of assembly gaps are likely to occur. In addition, since the disposition position of the above-mentioned vane 9 is close to the above-mentioned suction hole 52, a space for fixing screws cannot be ensured between the vane 9 and the suction hole 52. The surface pressure between the cross-sections of the sealing member 6 arranged in the axial direction decreases, which tends to cause leakage between the cross-sections. Simultaneously, when supporting the above-mentioned introduction pipe 81 with the connection pipe 82, the connection pipe 82 must also be fixed on the above-mentioned housing 1 toward the direction of the above-mentioned center line a, which makes the shape of the above-mentioned connection pipe must be a special shape, thus Conventional parts cannot be used, so common use of parts cannot be realized, and welding work is difficult to carry out.

For this reason, in the 2nd embodiment shown in Fig. 3, since this suction hole 52 is formed so that the center line d of the suction pipe connection side of the suction hole 52 faces the center of the cylinder, the direction of the suction hole 52 toward the cylinder The center line a of the opening side of the chamber 61 is inclined in the direction in which the tangent line b of the inner peripheral surface of the cylinder chamber 51 approaches, and when the suction pipe 8 is connected to the suction hole 52 via the introduction pipe 81, the Since the introduction pipe 81 is pressed in in the direction of the center line a, it is possible to eliminate the problem that occurs when the introduction pipe 81 is pressed in the same direction as the center line a. Therefore, not only can the flow resistance of sucking gaseous fluid be reduced and the pressure loss in the low-pressure chamber X be reduced, but also the problems of distortion of components and misalignment of assembly clearances can be prevented. Since the space between the disposition position of the above-mentioned partition plate 9 and the inlet side of the above-mentioned suction hole 52 can be ensured, a fixing member for connecting the above-mentioned closing member 6 and the cylinder 5 can be provided between the above-mentioned vane 9 and the suction hole 52. Screw B, and by screwing in this screw B, just can prevent each section between above-mentioned air cylinder 5 and closing member 6 from leaking. In addition, since the connection pipe 82 installed when the above-mentioned introduction pipe 81 is pressed in can also be connected toward the center of the above-mentioned cylinder 5, it can be used in common with the connection pipes used in the past, and the welding work is simple and easy. .

The third embodiment will be described below with reference to FIG. 4 and FIG. 5 . In the compressor, if the axial length of the compressor needs to be shortened or the axial dimension of the above-mentioned cylinder 5 and rotor 7 needs to be shortened to form a flat shape because a plurality of cylinders are required to constitute the compressor, in this case When the suction pipe 8 is connected downward to the cylinder 5, the diameter of the suction pipe 8 depends on the thickness of the cylinder 5. The thinner the thickness, the more restricted the size of the suction hole and affects the pressure loss. However, in the rotary compressor shown in FIGS. 4 and 5 , one of the above-mentioned closing members 6 , for example, the lower side closing member 6 , that is, the thickness of the rear end cover is increased, and a suction hole is formed on the rear end cover 6 . The passage 61, the suction passage 61 is formed as shown in FIG. 4, and its center line a is inclined in a direction in which the tangent line b of the imaginary intersection point between the inner peripheral surface of the cylinder chamber 51 and the center line a approaches. In addition, as shown in FIG. 5 As shown in FIG. Like the suction passage 61, the suction hole 52 provided on the cylinder 5 is formed so that its center line a is inclined in a direction in which the tangent line b of the inner peripheral surface of the cylinder chamber 51 approaches, and the suction hole 52 is formed as Inclining downward to connect with the top end side of the above-mentioned suction passage 61, it is possible to avoid loss of suction pressure due to restriction of the size of the suction hole.

That is to say, according to the above-mentioned structure, the size of the caliber of the above-mentioned suction passage 61 can be formed into a required sufficient size regardless of the thickness of the cylinder 5, and since the suction passage 61 is connected obliquely to the above-mentioned suction hole 52, it is possible to The suction air flow is smoothly introduced into the low-pressure chamber X in the above-mentioned cylinder chamber 51 from the suction passage 61 through the suction hole 52 under the condition of small flow resistance, which can not only reduce the pressure loss of the suction gaseous fluid in the low-pressure chamber X, but also avoid Insufficient amount of gaseous fluid sucked into the cylinder chamber 51 . That is to say, when the size of the cylinder 5 and the rotor 7 is reduced, the above structure can also smoothly introduce the intake air flow from the intake passage 61 to the cylinder chamber through the intake hole 52 under the condition of small flow resistance. In the low-pressure chamber X in the 51, the pressure loss of sucking gaseous fluid in the low-pressure chamber X can be reduced, and at the same time, the shortage of the amount of gaseous fluid sucked in the above-mentioned cylinder chamber 51 can also be avoided.

In addition, in the third embodiment, the blade 9 is integrally formed on a part of the rotor 7 in a protruding state together with the rotor 7 .

In addition, if a structure in which the suction pipe 8 is connected to the closure member 6 is adopted while shortening the axial dimension of the cylinder 5 and the rotor 7, it is preferable to use the fourth embodiment shown in FIG. The centerline of the inlet side of the suction passage 61 formed on the sealing member 6, which is connected to the suction pipe 8, faces the center of the cylinder chamber 51, and the centerline of the suction passage 61 connected to the suction hole 52 faces toward the center of the cylinder chamber 51. The suction hole 52 is inclined in a direction coincident with the centerline of the side opening to the cylinder chamber 51 . In this way, the suction pipe 8 can be connected toward the center of the cylinder 5 via the introduction pipe 81 as in the second embodiment. Therefore, a necessary amount of gaseous fluid corresponding to the volume of the cylinder chamber 51 can be introduced from the suction pipe 8 through the suction passage 61 and the suction hole 52 into the low-pressure chamber X in the cylinder chamber 51 with reduced flow resistance. , not only can reduce the pressure loss of the low-pressure chamber X, but also can prevent parts from twisting and assembly clearance dislocation, and can ensure a space for fixing screws between the position where the vane 9 is arranged and the suction hole 52, thereby preventing leakage.

In the above embodiments, the suction passage is formed in the lower side closing member 6, that is, the rear end cover, but the suction passage 61 may also be formed in the upper side closing member 6, that is, the front end cover. In addition, in a compressor that uses two cylinders, interposes an intermediate partition between the two cylinders, and compresses gaseous fluid in the cylinder chambers of the above-mentioned respective cylinders, the above-mentioned suction passage 61 may be formed in the above-mentioned middle. clapboard.

In addition, each of the above-mentioned embodiments has described the swing type rotary compressor. In the case of the structure belonging to this swing type rotary compressor, the above-mentioned rotor 7 does not rotate by itself but only revolves by the swing of the blades 9. Therefore, the position of the corresponding part of the rotor 7 and the above-mentioned suction hole 52 remains unchanged. Therefore, utilizing the revolution motion of the above-mentioned roller 7, as shown in FIG. An arc-shaped guide groove 71 is recessed inwardly at a position corresponding to the suction hole 52 to guide the suction gas introduced from the suction hole 52 into the above-mentioned low-pressure chamber X smoothly.

When adopting the above-mentioned structure, the space between the outlet of the suction hole 52 and the outer peripheral surface of the rotor 7 can be enlarged, and the suction resistance of the gaseous fluid sucked into the cylinder chamber 51 from the above-mentioned suction hole 52 can be reduced by using this space, and the The suction air flow from the suction hole 52 to the cylinder chamber 51 can be smoothly introduced into the low-pressure chamber X through the guide groove 71, thereby further reducing the flow resistance of the gaseous fluid sucked into the cylinder chamber 51, and making the suction The pressure loss of the gaseous fluid in the low-pressure chamber X is further reduced.

In addition, in the embodiment of FIG. 7 , since the guide groove 71 for guiding the gaseous fluid sucked in from the suction hole 52 is formed on the outer peripheral surface of the above-mentioned rotor 7 inwardly, it needs to be rocking, but In the above-mentioned first to fourth embodiments, the rocking type is not necessarily required, and the revolving type may also be used. In addition, in the above-mentioned third and fourth embodiments, the above-mentioned air cylinder and the roller are formed in a flat shape, but if the above-mentioned suction pipe 8 is connected to the above-mentioned closing member 6, the above-mentioned air cylinder 5 and rotor 7 do not necessarily have to be flat. flat.

Possibility of industrial use

The rotary compressor of the present invention can be mainly applied to refrigeration equipment.

Claims (5)

1. A rotary compressor comprising a cylinder (5) having a cylinder chamber (51) with a suction hole (52) and a discharge hole (53), and an eccentric shaft portion fitted on a drive shaft (3) (31) and the rotor (7) installed in the above-mentioned cylinder chamber (51), and the inside of the above-mentioned cylinder chamber (51) is divided into a low-pressure chamber (X) communicating with the above-mentioned suction hole (52) and the above-mentioned discharge chamber (X). The vane (9) of the high-pressure chamber (Y) through which the hole (53) communicates forms the above-mentioned suction hole (52) such that the centerline of the side of the suction hole (52) that opens to the above-mentioned cylinder chamber (51) (a) Inclining toward the vane (9) side with respect to a normal line (c) perpendicular to a tangent line (b) of a virtual intersection point of the center line (a) on the inner peripheral surface of the cylinder chamber (51). 2. The rotary compressor according to claim 1, wherein the centerline (d) of the side of the suction hole (52) connected to the suction pipe faces the center of the cylinder chamber (51). 3. The rotary compressor according to claim 1, on the closing member (6) attached to one side of the axial direction of the above-mentioned cylinder (5) and used to close one side of the axial direction of the above-mentioned cylinder (5) A suction passage (61) communicating with the suction pipe (8) is provided, and the tip side of the suction passage (61) is formed in an inclined shape toward the cylinder (5) and connected to the suction hole (52). 4. The rotary compressor according to claim 3, wherein the center line of the inlet side of the suction passage (61) formed on the sealing member (6) that communicates with the suction pipe (8) faces the cylinder chamber (51 ), the centerline of the side of the above-mentioned suction passage (61) connected to the above-mentioned suction hole (52) to the centerline of the side of the suction hole (52) that opens to the above-mentioned cylinder chamber (51) (a) Tilt in the same direction. 5. The rotary compressor according to claim 1, wherein the vane (9) is protrudingly coupled to the outer peripheral portion of the rotor (7), and a swing bush is swingably held on the cylinder (5) (10), the rocking bush (10) has a receiving groove (10a) capable of freely receiving the protruding tip side of the blade (9) in advance and retreat, and the suction hole ( 52) On the outer peripheral surface of the corresponding rotor (7), guide grooves (71) for guiding the sucked gaseous fluid introduced from the suction holes (52) to the low-pressure chamber (X) are formed inwardly.

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