JP3744533B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor, and in particular, a rotation provided with a cylinder having a cylinder chamber, a piston housed eccentrically in the cylinder chamber, and a pressing mechanism for bringing the cylinder side end plate and the piston side end plate close to each other. The present invention relates to a type compressor.

  Conventionally, as a rotary compressor provided with a compression mechanism in which a piston (eccentric rotating body) moves eccentrically in a cylinder chamber, the rotary compressor compresses refrigerant by changing the volume of the cylinder chamber accompanying the eccentric rotating motion of the annular piston. There exists a compressor (for example, refer patent document 1).

  As shown in FIGS. 12 and 13 (XIII-XIII cross-sectional view of FIG. 12), the compressor (100) includes a compression mechanism (120) and a compression mechanism (120) in a hermetic casing (110). And a drive mechanism (electric motor) (not shown) for driving.

  The compression mechanism (120) includes a cylinder (121) having an annular cylinder chamber (C1, C2) and an annular piston (122) disposed in the cylinder chamber (C1, C2). The cylinder (121) includes an outer cylinder (124) and an inner cylinder (125) arranged concentrically with each other, and the cylinder chamber (C1, C) between the outer cylinder (124) and the inner cylinder (125). C2) is formed. The outer cylinder (124) and the inner cylinder (125) are integrated by a cylinder side end plate (126A) provided on the upper end surface thereof.

  The annular piston (122) is connected to the eccentric part (133a) of the drive shaft (133) connected to the electric motor via a substantially circular piston base (piston side end plate) (126B), and is driven. An eccentric rotational movement is made with respect to the center of the shaft (133). Further, the annular piston (122) has one point on the outer peripheral surface substantially in contact with the inner peripheral surface of the outer cylinder (124). At the same time, one point on the inner peripheral surface is located on the outer peripheral surface of the inner cylinder (125) at a position that is 180 ° out of phase with this contact point. It is configured to perform an eccentric rotational motion while maintaining a substantially contacting state. As a result, an outer cylinder chamber (C1) is formed outside the annular piston (122), and an inner cylinder chamber (C2) is formed inside.

  An outer blade (123A) is disposed outside the annular piston (122). The outer blade (123A) is biased toward the radially inner side of the annular piston (122), and the inner peripheral end is in pressure contact with the outer peripheral surface of the annular piston (122). The outer blade (123A) divides the outer cylinder chamber (C1) into a high pressure chamber (first chamber) (C1-Hp) and a low pressure chamber (second chamber) (C1-Lp).

  On the other hand, an inner blade (123B) is disposed on the extended line of the outer blade (123A) inside the annular piston (123). The inner blade (123B) is biased toward the radially outer side of the annular piston (122), and the outer peripheral end is in pressure contact with the inner peripheral surface of the annular piston (122). The inner blade (123B) divides the inner cylinder chamber (C2) into a high pressure chamber (first chamber) (C2-Hp) and a low pressure chamber (second chamber) (C2-Lp).

  The outer cylinder (124) has a suction port (141) communicating with the outer cylinder chamber (C1) from the suction pipe (114) provided in the casing (110) in the vicinity of the outer blade (123A). Yes. The annular piston (122) has a through hole (143) in the vicinity of the suction port (141), and the through hole (143) allows the low pressure chamber (C1-Lp) of the outer cylinder chamber (C1). And the low pressure chamber (C2-Lp) of the inner cylinder chamber (C2) communicate with each other. Further, the compression mechanism (120) has a discharge port (C1 and C2) for communicating the high pressure chambers (C1-Hp, C2-Hp) of the cylinder chambers (C1, C2) with the high pressure space (S) in the casing (110) ( (Not shown) is provided.

  In the compressor (100) configured as described above, when the drive shaft (133) rotates and the annular piston (122) rotates eccentrically, both the outer cylinder chamber (C1) and the inner cylinder chamber (C2) The expansion and reduction of the volume are repeated alternately. When the volumes of the cylinder chambers (C1, C2) are expanded, a suction stroke for sucking refrigerant into the cylinder chambers (C1, C2) from the suction port (141) is performed, while the volumes are reduced. Includes a compression stroke in which the refrigerant is compressed in each cylinder chamber (C1, C2), and the refrigerant is discharged from each cylinder chamber (C1, C2) to the high-pressure space (S) in the casing (110) through the discharge port. And a discharge stroke to be performed. As described above, the high-pressure refrigerant discharged into the high-pressure space (S) of the casing (110) flows out to the condenser of the refrigerant circuit via the discharge pipe (115) provided in the casing (110). To do.

In the compressor (100) of this example, a support plate (117) for supporting the end plate (126B) is formed on the lower surface side of the piston end plate (126B) to which the annular piston (122) is connected. ing. A seal ring (129) concentric with the center of the annular piston (122) is provided at the facing portion where the piston side end plate (126B) and the support plate (117) face each other. Then, the pressure of the refrigerant in the high-pressure space (S) is applied to the piston side end plate (126B) on the inner peripheral side of the seal ring (129). By doing this, the piston side end plate (126B) is pushed up in the axial direction and pushed toward the cylinder (121), and the axial clearance between the cylinder (121) and the annular piston (123) (below the cylinder (121) in the axial direction). The first axial gap between the end face and the piston end plate (126B) and the second axial gap between the upper end face in the axial direction of the piston (122) and the cylinder end plate (126A) are reduced. Yes.
JP-A-6-288358

  Incidentally, in the conventional configuration shown in FIGS. 12 and 13, for example, when the pressure in the cylinder chamber (C1, C2) increases during the compression stroke, the piston side end plate (126B formed on the lower end portion of the annular piston (122) is provided. ) Tends to act on the axial gas force (downward thrust load). Here, when this thrust load becomes large or the point of action of the thrust load moves away from the axis of the drive shaft (133), the moment (overturning moment) acting on the piston side end plate (126B) exceeds a predetermined value. There is a possibility that the piston-side end plate (126B) and the annular piston (122) fixed to the end plate (126B) may be inclined (rolled over) with respect to the drive shaft (133). When a gap is generated between the annular piston (122) and the cylinder (121) due to the overturning of the annular piston (122), the refrigerant leaks from the gap and the compression efficiency is impaired.

  Here, in this conventional configuration, the axial pressing force obtained by the pressure on the inner peripheral surface of the seal ring (129) provided on the piston side end plate (126B) resists the thrust load, and the piston side end plate ( 126B) is considered to reduce the rollover moment resulting from the thrust load, but the reduction action is insufficient as described below.

  FIG. 14 is an explanatory view showing stepwise the eccentric motion of the annular piston (122) in the conventional configuration. When the annular piston (122) is driven by the drive shaft (133), it rotates eccentrically within the cylinder chamber (C1, C2) in the order shown in FIGS. Here, when the annular piston (122) is in, for example, the state (A), the pressure of the refrigerant in the high pressure chamber (C2-Hp) of the inner cylinder chamber (C2) increases. As a result, the center of the thrust load (PT) acts closer to the high pressure chamber (C2-Hp) in the radial direction on the upper surface of the piston side end plate (126B) as shown by the arrow (PT) in FIG. The center of the axial pressing force (arrow (P) in FIG. 14) obtained by the seal ring (129) against the thrust load (PT) is the center of the seal ring (129) on the lower surface of the piston side end plate (126B). It acts on the position, in other words, the center position of the annular piston (122). However, in this case, the point of action of the thrust load (PT) acting on the piston side end plate (126B) and the point of action of the axial pressing force (P) are displaced from each other in the radial direction. It becomes difficult to reduce the moment effectively.

  Further, the internal pressure of the high pressure chamber (C2-Hp) in the inner cylinder chamber (C2) is increased, and the internal pressure of the high pressure chamber (C1-Hp) in the outer cylinder chamber (C1) is slightly increased, as shown in FIG. Then, the thrust load (PT) acts closer to the high pressure chamber (C1-Hp, C2-Hp), whereas the axial pressing force (P) obtained by the seal ring (129) is the annular piston (122). Acts closer to the low pressure chamber (C2-Lp), which is the center position of. For this reason, the point of action of the thrust load (PT) and the point of action of the axial pressing force (P) are further deviated, and it is further difficult to reduce the rollover moment.

  Further, for example, the internal pressure of the high pressure chamber (C1-Hp) of the outer cylinder (C1) is increased, and the internal pressure of the high pressure chamber (C2-Hp) of the inner cylinder chamber (C2) is slightly increased, as shown in FIG. Since the center of thrust load (PT) acts closer to the high pressure chamber (C1-Hp, C2-Hp), the point of action of thrust load (PT) and the point of action of axial pressing force (P) As a result, it is difficult to effectively reduce the capsize moment.

  As described above, in the conventional configuration, when the annular piston (122) rotates eccentrically, the axial pressing force (P) obtained by the seal ring (129) does not easily match the thrust load (PT). There is a problem that the overturning of the annular piston (122) cannot be effectively suppressed.

  The present invention was devised in view of such problems, and an object thereof is to form an annular shape by effectively applying an axial pressing force to a thrust load acting on the end plate of the eccentric rotating body. It is to suppress the overturn of an eccentric rotating body such as a piston.

  In the present invention, the axial pressing force applied to the end plate is made to act eccentric from the center of the eccentric rotating body.

Specifically, in the first invention, the cylinder (21) having the cylinder chamber (C) (C1, C2) and the cylinder chamber (C) (C1, C2) are stored eccentrically with respect to the cylinder (21). The piston (22) is disposed in the cylinder chamber (C) (C1, C2), and the cylinder chamber (C) (C1, C2) is connected to the first chamber (C-Hp) (C1-Hp, C2- Hp) and a blade (23) partitioned into a second chamber (C-Lp) (C1-Lp, C2-Lp), and at least one of the cylinder (21) and the piston (22) is eccentric. A compression mechanism (20) that rotates eccentrically as a rotating body (21, 22), a drive shaft (33) that drives the compression mechanism (20), and axial directions of the cylinder chambers (C) (C1, C2) Cylinder side end plate (26A) provided on one end side and facing the axial end face of piston (22), and provided on the other axial end side of cylinder chamber (C) (C1, C2) Opposite the axial end face The pressing mechanism (60) for bringing the piston side end plate (26B) close to each other in the axial direction of the drive shaft (33), the compression mechanism (20), the drive shaft (33), and the pressing mechanism (60) are housed. A rotary compressor with a casing (10) is assumed. In this rotary compressor, the pressing mechanism (60) is eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22) and from the center of the drive shaft (33). The position is the center of the axial pressing force, and the compression mechanism (20) has a discharge port that discharges the fluid compressed in the cylinder chamber (C1, C2) to the outside of the compression mechanism (20). 45, 46) is formed, and the pressing mechanism (60) is located outside the locus whose radius is the amount of eccentricity of the eccentric rotating body (21, 22) with respect to the center of the drive shaft (33), and the eccentric rotating body (21, 22) characterized in that the position eccentric from the center of the end plate (26A, 26B) toward the discharge port (45, 46) is the center of action of the axial pressing force It is. In the following description, “the position eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22) and eccentric from the center of the drive shaft (33)” is referred to as “the eccentric rotating body (21, 22). 22) Abbreviated as “the position eccentric from the center of the end plate (26A, 26B)”.

  In the first aspect of the invention, the eccentric rotator (21, 22) is eccentrically rotated by the drive shaft (33), whereby the first chamber (C-Hp) formed in the cylinder chamber (C) (C1, C2). ) The volume of (C1-Hp, C2-Hp) and the second chamber (C-Lp) (C1-Lp, C2-Lp) changes, and the fluid to be treated is compressed. At this time, the piston end plate (26B) and the cylinder end plate (26A) are brought close to each other in the axial direction by the pressing mechanism (60), so that the axial direction between the piston (22) and the cylinder (21) is increased. A gap (a first axial gap between the axial end surface of the cylinder (21) and the piston side end plate (26B) and a second between the axial end surface of the piston (22) and the cylinder side end plate (26A) (The axial gap) is reduced.

  Here, in the present invention, the center of the resultant force of the axial pressing force obtained by the pressing mechanism (60) is applied to a position that is eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22). I am doing so. Therefore, unlike the above-described prior art, it is possible to prevent the thrust load (PT) action point and the axial pressing force (P) action point from shifting in the axial direction. As a result, the thrust load (PT ) Can be effectively suppressed.

In the present invention, the compression mechanism (20) is formed with discharge ports (45, 46) for discharging the fluid compressed in the cylinder chambers (C1, C2) to the outside of the compression mechanism (20). (60) is outside the locus having the radius of the eccentric rotor (21, 22) as a radius with respect to the center of the drive shaft (33), and the end plate (26A, 26) of the eccentric rotor (21, 22). The position eccentric from the center of 26B) toward the discharge port (45, 46) is the center of action of the axial pressing force.

In the present invention, for example, the fluid to be processed which has been compressed in the first chamber (C1-Hp, C2-Hp) and becomes high pressure is discharged from the discharge port (45, 46) to the outside of the compression mechanism (20).

Here, in the present invention, in particular, the pressure of the fluid to be treated tends to be high, and the thrust load (PT) acting on the end plate (26A, 26B) of the eccentric rotating body (21, 22) is also likely to increase. 21 and 22) are located near the discharge port (45, 46) in the end plate (26A, 26B) at the center where the resultant axial pressing force acts. Therefore, the point of application of thrust load (PT) and the point of application of axial pressing force (P) can be easily matched in the axial direction, and as a result, the rollover moment caused by thrust load (PT) can be more effectively suppressed. can do.

According to a second aspect of the present invention, in the rotary compressor according to the first aspect, the cylinder chamber (C) has a circular cross-sectional shape perpendicular to the axis, and the piston (22) is disposed in the cylinder chamber (C). It is characterized by comprising a piston (22). Note that the “axis-perpendicular section” referred to here is a section perpendicular to the drive shaft (rotation center).

According to the second aspect of the present invention, in the rotary compressor in which the cross-sectional shape perpendicular to the axis of the cylinder chamber (C) is circular and the piston (22) is constituted by the circular piston (22), the pressing mechanism (60) The center of the resultant axial pressing force is applied to a position that is eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22), so the operating point of the thrust load (PT) And the point of application of the axial pressing force (P) can be prevented from shifting in the axial direction, and as a result, the rollover moment due to the thrust load (PT) can be effectively suppressed.

According to a third invention, in the rotary compressor according to the first invention, the cylinder chamber (C1, C2) has an annular cross section perpendicular to the axis, and the piston (22) is in the cylinder chamber (C1, C2). It is characterized by comprising an annular piston (22) which is arranged and partitions the cylinder chambers (C1, C2) into an outer cylinder chamber (C1) and an inner cylinder chamber (C2).

In the third aspect of the invention, by arranging the annular piston (22) in the annular cylinder chamber (C1, C2), the outer peripheral wall surface of the cylinder chamber (C1, C2) and the outer periphery of the annular piston (22) An outer cylinder chamber (outer cylinder chamber) (C1) can be formed between the inner cylinder chamber (outside cylinder chamber) (C1) and an inner cylinder chamber ( Inner cylinder chamber (C2) can be formed. That is, like the conventional rotary compressor described above, the fluid to be processed is compressed by alternately repeating the expansion and reduction of the volume in both the outer cylinder chamber (C1) and the inner cylinder chamber (C2). A rotary compressor can be constructed.

In the present invention, as in the first and second inventions, the center of the resultant force of the axial pressing force obtained by the pressing mechanism (60) is used as the end plate (26A, 26B) of the eccentric rotating body (21, 22). ), It can be prevented from shifting in the axial direction between the point of application of thrust load (PT) and the point of application of axial pressing force (P). The overturning moment resulting from the thrust load (PT) can be effectively suppressed.

According to a fourth aspect of the present invention, in the rotary compressor according to the third aspect of the invention, the piston (22) is formed in a C-shape with a part of the annular ring divided, and a blade ( 23) A oscillating bush (27) having a blade groove (28) that can be moved back and forth is slidably held, and the blade (23) is disposed on the inner peripheral side of the annular cylinder chamber (C1, C2). From the wall surface to the outer peripheral wall surface, the blade groove (28) is inserted and extended.

In the fourth aspect of the invention, when at least one of the cylinder (21) or the piston (22) moves eccentrically as the eccentric rotating body (21, 22), the blade (23) is moved to the blade groove (28) of the swing bush (27). The swinging bush (27) swings while being in surface contact at the part where the piston (22) is divided. Therefore, the cylinder chambers (C1, C2) are moved into the first chamber (C1-Hp, C2-Hp) and the second chamber (c1) while smoothly operating the blade (23) during the eccentric motion of the eccentric rotating body (21, 22). C1-Lp, C2-Lp).

According to a fifth aspect of the present invention, in the rotary compressor according to any one of the first to fourth aspects, the casing (10) includes a cylinder chamber (26A, 26B) of the end plate (26A, 26B) of the eccentric rotating body (21, 22). A support plate (17) is disposed along the opposite surface of the C1, C2) surface, and the end plate (26A, 26B) of the eccentric rotating body (21, 22) and one of the support plate (17) are provided with the end plate. (26A, 26B) and a support ring (17) facing part (61, 62) is separated into an inner and outer radial direction, a seal ring (1) and a second facing part (62) 29) is provided at a position eccentric from the center of the eccentric rotating body (21, 22), and the pressing mechanism (60) applies the pressure of the fluid discharged to the outside of the compression mechanism (20) to the end plate (26A, 26B) It is comprised so that it may act on the 1st opposing part (61) in.

In the fifth invention, the eccentric rotating body (21, 22) is provided by providing the seal ring (29) between the end plate (26A, 26B) and the support plate (17) of the eccentric rotating body (21, 22). ) Between the end plate (26A, 26B) and the support plate (17) is divided into two or more facing portions (61, 62). Here, the fluid that has been pressurized by the compression mechanism (20) is introduced into the first opposing portion (61), and the pressure of this fluid is applied to the first opposing portion of the end plate (26A, 26B) of the eccentric rotating body (21, 22). By acting on the portion (61), an axial pressing force of the eccentric rotating body (21, 22) against the end plate (26A, 26B) can be obtained.

  In the present invention, the seal ring (29) is provided at a position eccentric from the center of the eccentric rotating body (21, 22). For this reason, the center of the axial pressing force obtained by the seal ring (29) acts at a position eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22). Therefore, as described above, it is possible to suppress a deviation in the axial direction between the operating point of the thrust load (PT) and the operating point of the axial pressing force (P).

According to a sixth aspect of the present invention, in the rotary compressor according to the fifth aspect , the seal ring (29) is an annular groove formed in either the eccentric rotating body (21, 22) or the support plate (17). 17b) is featured.

In the sixth aspect of the invention, the seal ring (29) is fitted into the annular groove (17b), so that the seal ring (29) is reliably located at a position eccentric from the center of the eccentric rotating body (21, 22). Can hold.

A seventh aspect of the invention is the rotary compressor according to any one of the first to fourth aspects of the invention, on the surface opposite to the cylinder chamber (C1, C2) side surface of the end plate (26A) of the eccentric rotating body (21). In addition, a slit (63) is formed at a position eccentric from the center of the eccentric rotating body (21), and the pressing mechanism (60) applies the pressure of the fluid discharged to the outside of the compression mechanism (20) to the slit (63). It is comprised so that it may act on.

In the seventh aspect of the invention, the pressure of the fluid that has been increased by the compression mechanism (20) is applied to the slit (63), so that the shaft is placed near the slit (63) in the end plate (26A) of the eccentric rotating body (21). Direction pressing force (P) is likely to act. Here, in the present invention, the slit (63) is formed at a position eccentric from the center of the eccentric rotating body (21). For this reason, the center of the axial pressing force obtained by forming the slit (63) acts at a position eccentric from the center of the eccentric rotating body (21) in the end plate (26A). Therefore, as described above, it is possible to suppress a deviation in the axial direction between the operating point of the thrust load (PT) and the operating point of the axial pressing force (P).

The eighth invention is the rotary compressor according to any one of the first to fourth inventions, wherein the end face (26A) of the eccentric rotor (21) is opposite to the cylinder chamber (C1, C2) side. And the groove part (65) formed in the position eccentric from the center of the eccentric rotating body (21), and the end plate (26A) so that the groove part (65) and the cylinder chamber (C) (C1, C2) communicate with each other The pressing mechanism (60) introduces part of the fluid compressed in the cylinder chamber (C1, C2) into the groove (65) from the through hole (64). And it is comprised so that the pressure of this fluid may act on the said groove part (65).

In the eighth aspect of the invention, part of the fluid compressed by the compression mechanism (20) is introduced into the groove (65) through the through hole (64), and the groove (65 in the end plate (26A) of the eccentric rotating body (21) ) Axial pressing force tends to act in the vicinity. Here, in this invention, the said groove part (65) is formed in the position eccentric from the center of the eccentric rotary body (21). For this reason, the center of the axial pressing force obtained by the formation of the groove (65) acts at a position eccentric from the center of the eccentric rotating body (21) in the end plate (26A). Therefore, as described above, it is possible to suppress a deviation in the axial direction between the operating point of the thrust load (PT) and the operating point of the axial pressing force (P).

According to a ninth aspect of the present invention, in the rotary compressor according to any one of the first to eighth aspects, the first axial clearance between the axial end surface of the cylinder (21) and the piston side end plate (26B) and the piston A seal mechanism (71, 72, 73) that suppresses fluid leakage in at least one of the second axial gaps between the axial end face of (22) and the cylinder side end plate (26A) is provided. To do.

In the ninth aspect of the invention, a sealing mechanism for reducing the axial clearance between the cylinder (21) and the piston (22) is provided in addition to the pressing mechanism (60) described above, so that the eccentric rotating body (21, 22) is provided. During the eccentric motion, for example, it is possible to suppress the fluid that has become high pressure in the first chamber (C1-Hp, C2-Hp) from leaking into the second chamber (C1-Lp, C2-Lp) through the axial gap.

According to a tenth aspect of the present invention, in the rotary compressor according to the ninth aspect , the seal mechanism is constituted by a tip seal (71, 72, 73) provided in at least one of the first axial gap and the second axial gap. It is characterized by being.

  In the tenth aspect of the present invention, the tip seal (71, 72, 73) is provided in at least one of the first axial gap and the second axial gap between the cylinder (21) and the piston (22). This axial gap is reduced, and fluid leakage in this gap can be suppressed.

The eleventh aspect of the invention is the rotary compressor having the same configuration as that of the first aspect of the invention, wherein the pressing mechanism (60) is eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22). And the position eccentric from the center of the drive shaft (33) is the center of action of the axial pressing force, and the cylinder chamber (C1, C2) side of the end plate (26A) of the eccentric rotating body (21) The slit (63) is formed on the opposite side of the surface and at a position eccentric from the center of the eccentric rotating body (21), and the pressing mechanism (60) reduces the pressure of the fluid discharged to the outside of the compression mechanism (20). It is configured to act on the slit (63).

  According to the first invention, in the compression mechanism (20) including the cylinder (21) having the cylinder chambers (C1) (C1, C2) and the piston (22), the piston (22) is pressed by the pressing mechanism (60). The thrust clearance (PT) generated in the cylinder chamber (C) (C1, C2) is reduced by reducing the axial clearance between the cylinder and the cylinder (21) and by the eccentric rotor (21, 22) moving eccentrically. An opposing axial pressing force (P) can be applied. Here, the axial pressing force (P) is decentered from the center of the eccentric rotating body (21, 22) and applied to the end plate (26A, 26B), so that the thrust load (PT) and the axial pressing force (P ) In the radial direction can be reduced, and the rollover moment can be effectively suppressed.

In addition, the axial pressing force (P) against the end plate (26A, 26B) obtained by the pressing mechanism (60) is applied to the discharge port (45, 46) where the thrust load (PT) easily acts in the cylinder chamber (C1, C2). ) I try to work closer. For this reason, the point of action of the thrust load (PT) and the axial pressing force (P) can be brought close to each other, and the rollover moment can be further effectively reduced.

According to the second invention, in the compression mechanism (20) having the cylinder (21) having the circular cylinder chamber (C1) and the circular piston (22), the pressing mechanism (60) Axial pressing force against thrust load (PT) generated in the cylinder chamber (C1) due to eccentric movement of the eccentric rotating body (21, 22) while reducing the axial clearance with the cylinder (21) (P) can act. Here, the axial pressing force (P) is decentered from the center of the eccentric rotating body (21, 22) and applied to the end plate (26A, 26B), so that the thrust load (PT) and the axial pressing force (P ) In the radial direction can be reduced, and the rollover moment can be effectively suppressed.

According to the third aspect of the present invention, in the compression mechanism (20) including the cylinder (21) having the annular cylinder chambers (C1, C2) and the annular piston (22), the piston (22 ) And the cylinder (21) is reduced, and the eccentric rotating body (21, 22) moves eccentrically to resist the thrust load (PT) generated in the cylinder chamber (C1, C2). An axial pressing force (P) can be applied. Here, the axial pressing force (P) is decentered from the center of the eccentric rotating body (21, 22) and applied to the end plate (26A, 26B), so that the thrust load (PT) and the axial pressing force (P ) In the radial direction can be reduced, and the rollover moment can be effectively reduced.

According to the fourth aspect of the invention, in the rotary compressor of the third aspect of the invention, the blade (23) is advanced and retracted while being in surface contact within the blade groove (28) of the swing bush (27), and at the same time, the piston ( By swinging the swing bush (27) at the part 22), the eccentric rotator (21, 22) can smoothly rotate eccentrically while partitioning the cylinder chamber (C1, C2). Therefore, seizure and wear at the contact portion between the blade (23) and the swing bush (27) can be suppressed, and the first chamber (C1-Hp, C2-Hp) and the second chamber (C1-Lp, C2-Lp) ) Can also be prevented from leaking gas.

According to the fifth aspect of the present invention, the pressing mechanism (60) is moved by applying the pressure of the high-pressure fluid to the end plate (26A, 26B) in the first facing portion (61) defined by the seal ring (29). It can be configured. Here, the pressing mechanism (60) can be easily configured by decentering the seal ring (29) from the center of the eccentric rotating body (21, 22), and the rollover moment can be effectively reduced. That is, the effect of reducing the rollover moment can be obtained with a simple structure.

  Further, by providing the seal ring (29), the refrigerant in the cylinder chamber (C) (C1, C2) is allowed to flow between the first facing portion (61) between the support plate (17) and the end plate (26A, 26B). ) Can be prevented from leaking outside the compression mechanism (20).

According to the sixth aspect of the invention, the annular ring (17b) is formed in the piston (22) or the support plate (17), so that the seal ring (29) is securely positioned while positioning the seal ring (29). Can be held in.

According to the seventh aspect , the pressing mechanism (60) can be configured by applying a high-pressure fluid pressure to the slit (63) formed in the end plate (26A). Here, the pressing mechanism (60) can be easily configured by decentering the slit (63) from the center of the eccentric rotating body (21), and the rollover moment can be effectively reduced. That is, the effect of reducing the rollover moment can be obtained with a simple structure.

  Further, since the slit (63) can be easily formed by providing a step on the end plate (26A), for example, the end plate (26A) having the eccentric rotating body (21) formed with the slit (63) is sintered or It can be integrally formed by forging.

According to the eighth aspect of the present invention, the pressing mechanism (60) is moved by causing a part of the fluid compressed in the cylinder chamber (C1, C2) to act on the groove (65) through the through hole (64). It can be configured. Here, the pressing mechanism (60) can be easily configured by decentering the groove (65) from the center of the eccentric rotating body (21), and the rollover moment can be effectively reduced.

  Further, according to the present invention, when the pressure in the cylinder chamber (C1, C2) increases and the thrust load (PT) increases, the axial pressing force (P) acting on the groove (65) is also increased. On the other hand, when the thrust load (PT) becomes small, the axial pressing force (P) can be made small. Therefore, it is possible to suppress an increase in mechanical loss of the eccentric rotating body (21) due to the excess axial pressing force (P), and to effectively reduce the overturning moment.

According to the ninth and tenth aspects of the present invention, by providing the seal mechanism (71, 72, 73) separately from the pressing mechanism (60), the axial gap between the cylinder (21) and the piston (22) is provided. Fluid leakage can be suppressed and compression efficiency can be further improved.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1 of the Invention
The compressor according to the first embodiment is a rotary compressor that compresses a fluid by expanding and contracting a volume in a cylinder chamber, which will be described later, by an eccentric rotating body performing an eccentric rotational motion. The rotary compressor is connected to a refrigerant circuit of an air conditioner, for example, and is used for compressing the refrigerant sucked from the evaporator and discharging it to the condenser.

  As shown in FIG. 1, the rotary compressor (1) includes a casing (10) in which a compression mechanism (20) and an electric motor (drive mechanism) (30) are housed, and is configured as a completely sealed type. Yes.

  The casing (10) includes a cylindrical body (11), an upper end panel (12) fixed to the upper end of the body (11), and a lower end panel fixed to the lower end of the body (11). (13). The upper end plate (12) is provided with a suction pipe (14) passing through the upper end plate (12). On the other hand, the body (11) is provided with a discharge pipe (15) penetrating the body (11).

  The compression mechanism (20) is provided on the upper side in the casing (10). The compression mechanism (20) is configured between an upper housing (16) fixed to the casing (10) and a lower housing (support plate) (17). The compression mechanism (20) includes a cylinder (21) having a cylinder chamber (C1, C2) having an annular cross section perpendicular to the axis, and an annular piston (piston) (22) disposed in the cylinder chamber (C1, C2). ) And cylinder chambers (C1, C2) are the first chamber, the high pressure chamber (compression chamber) (C1-Hp, C2-Hp) and the second chamber, the low pressure chamber (suction chamber) (C1-Lp, C2-) Lp) (see FIG. 2). Further, a cylinder side end plate (26A) is formed at the lower end of the cylinder (21), and the cylinder side end plate (26A) faces the cylinder chambers (C1, C2). In the present embodiment, the cylinder (21) is configured to perform an eccentric rotational motion as an eccentric rotating body.

  An electric motor (30) is provided near the lower side in the casing (10). The electric motor (30) includes a stator (31) and a rotor (32). The stator (31) is fixed to the inner wall of the body (11) of the casing (10). The rotor (32) is connected to the drive shaft (33), and the drive shaft (33) is configured to rotate together with the rotor (32).

  The drive shaft (33) extends in the vertical direction from the vicinity of the lower end plate (13) to the vicinity of the upper end plate (12). An oil supply pump (34) is provided at the lower end of the drive shaft (33). The oil supply pump (34) is connected to an oil supply passage (not shown) that extends upward in the drive shaft (33) and communicates with the compression mechanism (20). The oil supply pump (34) is configured to supply the lubricating oil stored at the bottom in the casing (10) to the sliding portion of the compression mechanism (20) through the oil supply passage.

  The drive shaft (33) is formed with an eccentric portion (33a) at a portion located in the cylinder chamber (C1, C2). The eccentric part (33a) is formed to have a larger diameter than the upper and lower parts of the eccentric part (33a), and is eccentric from the axis of the drive shaft (33) by a predetermined amount.

  The cylinder (21) includes an outer cylinder (24) and an inner cylinder (25). The outer cylinder (24) and the inner cylinder (25) are integrated by connecting the lower end portions thereof with the cylinder side end plate (26A). The inner cylinder (25) is slidably fitted in the eccentric part (33a) of the drive shaft (33).

  The annular piston (22) is formed integrally with the upper housing (16) and has a piston side end plate (26B). The upper housing (16) and the lower housing (17) are formed with bearing portions (16a, 17a) for supporting the drive shaft (33), respectively. Thus, in the compressor (1) of the present embodiment, the drive shaft (33) penetrates the cylinder chamber (C1, C2) in the vertical direction, and both axial portions of the eccentric portion (33a) are bearing portions. It has a through shaft structure that is held by the casing (10) via (16a, 17a).

  Further, in the compression mechanism (20), the cylinder side end plate (26A) is provided on one end side (lower end side) in the axial direction of the cylinder chamber (C1, C2) and faces the lower end surface in the axial direction of the piston (22). The piston end plate (26B) is provided on the other axial end (upper end) of the cylinder chamber (C1, C2) and is configured to face the upper axial end surface of the cylinder (21). .

  As shown in FIG. 2, the compression mechanism (20) includes an oscillating bush (27) for movably connecting the annular piston (22) and the blade (23) to each other. The annular piston (22) is formed in a C shape in which a part of the annular ring is divided. The blade (23) is located on the radial line of the cylinder chamber (C1, C2), from the inner peripheral wall surface (the outer peripheral surface of the inner cylinder (25)) of the cylinder chamber (C1, C2) to the outer peripheral wall surface (outer side). The cylinder (24) is configured so as to extend through the part where the annular piston (22) is divided, and is fixed to the outer cylinder (24) and the inner cylinder (25). The swinging bush (27) connects the annular piston (22) and the blade (23) at a parting point of the annular piston (22). The blade (23) may be formed integrally with the outer cylinder (24) and the inner cylinder (25), or another member may be formed integrally with both cylinders (24, 25).

  The inner peripheral surface of the outer cylinder (24) and the outer peripheral surface of the inner cylinder (25) are cylindrical surfaces arranged on the same center, and the cylinder chambers (C1, C2) are formed therebetween. The annular piston (22) has an outer peripheral surface having a smaller diameter than the inner peripheral surface of the outer cylinder (24) and an inner peripheral surface having a larger diameter than the outer peripheral surface of the inner cylinder (25). Thus, an outer cylinder chamber (C1) is formed between the outer peripheral surface of the annular piston (22) and the inner peripheral surface of the outer cylinder (24), and the inner peripheral surface of the annular piston (22) and the inner cylinder (25 ) Is formed between the inner cylinder chamber (C2).

  In addition, the annular piston (22) and the cylinder (21) are in a state in which the outer peripheral surface of the annular piston (22) and the inner peripheral surface of the outer cylinder (24) are substantially in contact at one point (strictly, a clearance in the micron order) In the state where refrigerant leakage in the gap is not a problem), the inner peripheral surface of the annular piston (22) and the outer peripheral surface of the inner cylinder (25) It comes to substantially touch at one point.

  The swing bush (27) includes a discharge side bush (27A) located on the high pressure chamber (C1-Hp, C2-Hp) side with respect to the blade (23), and a low pressure chamber (C1 -Lp, C2-Lp) and suction side bush (27B). The discharge-side bush (27A) and the suction-side bush (27B) are both substantially semicircular in cross section and formed in the same shape, and are arranged so that the flat surfaces face each other. And the space between the opposing surfaces of both bushes (27A, 27B) constitutes a blade groove (28).

  The blade (23) is inserted into the blade groove (28), the flat surface of the oscillating bush (27A, 27B) is substantially in surface contact with the blade (23), and the arc-shaped outer peripheral surface is the annular piston (22). Is substantially in surface contact. The swing bushes (27A, 27B) are configured such that the blade (23) advances and retreats in the blade groove (28) in the surface direction with the blade (23) sandwiched between the blade grooves (28). . At the same time, the swing bushes (27A, 27B) are configured to swing integrally with the blade (23) with respect to the annular piston (22). Therefore, the swing bush (27) is configured such that the blade (23) and the annular piston (22) can swing relatively with the center point of the swing bush (27) as the swing center, and the blade (23) is configured to be movable back and forth in the surface direction of the blade (23) with respect to the annular piston (22).

  In this embodiment, an example in which both bushes (27A, 27B) are separated from each other has been described. However, both bushes (27A, 27B) may be integrated with each other.

  In the above configuration, when the drive shaft (33) rotates, the outer cylinder (24) and the inner cylinder (25) move the blade (23) while the blade (23) advances and retreats in the blade groove (28). Oscillates with the center point as the oscillation center. By this swinging operation, the cylinder (21) rotates (revolves) while being eccentric with respect to the drive shaft (33) (see FIGS. 3A to 3D).

  As shown in FIG. 1, a suction port (41) is formed in the upper housing (16) at a position below the suction pipe (14). The suction port (41) is formed in a long hole shape from the inner cylinder chamber (C2) to the suction space (42) formed on the outer periphery of the outer cylinder (24). The suction port (41) penetrates the upper housing (16) in its axial direction, and the low pressure chambers (C1-Lp, C2-Lp) and the suction space (42) of the cylinder chambers (C1, C2) and the upper housing ( It communicates with the space above 16) (low pressure space (S1)). The outer cylinder (24) has a through hole (43) communicating the suction space (42) with the low pressure chamber (C1-Lp) of the outer cylinder chamber (C1). Is formed with a through hole (44) communicating the low pressure chamber (C1-Lp) of the outer cylinder chamber (C1) and the low pressure chamber (C2-Lp) of the inner cylinder chamber (C2).

  The upper housing (16) is formed with discharge ports (45, 46). Each of these discharge ports (45, 46) penetrates the upper housing (16) in the axial direction thereof. The lower end of the discharge port (45) opens to the high pressure chamber (C1-Hp) of the outer cylinder chamber (C1), and the lower end of the discharge port (46) is the high pressure chamber (C2-Hp) of the inner cylinder chamber (C2). ). On the other hand, the upper ends of these discharge ports (45, 46) communicate with the discharge space (49) via discharge valves (reed valves) (47, 48) that open and close the discharge ports (45, 46). .

  The discharge space (49) is formed between the upper housing (16) and the cover plate (18). The upper housing (16) and the lower housing (17) are formed with a discharge passage (49a) that communicates from the discharge space (49) to the space below the lower housing (17) (high pressure space (S2)).

  As a feature of the present invention, the cylinder side end plate (26A) and the piston side end plate (26B) are disposed between the cylinder side end plate (26A) and the lower housing (17). A pressing mechanism (60) is provided to be close to each other in the axial direction. Specifically, the pressing mechanism (60) is composed of a seal ring (29) provided in an opposing portion (61, 62) between the lower housing (17) and the cylinder side end plate (26A). Yes. The seal ring (29) is fitted in an annular groove (17b) formed in the lower housing (17), and seals the facing portion between the cylinder side end plate (26A) and the lower housing (17). The ring (29) is partitioned into a radially inner facing portion (first facing portion) (61) and a radially outer facing portion (second facing portion) (62) of the seal ring (29).

  The seal ring (29) is arranged so that its center is eccentric from the center of the cylinder (21) fitted in the eccentric part (33a) of the drive shaft (33) toward the discharge port (45, 46) described above. (See FIG. 2). In other words, the rotational direction of the eccentric rotating body (cylinder (21) in the present embodiment) with the direction (X axis shown in FIG. 2) extending from the center of the drive shaft (33) to the blade (23) as the reference angle of 0 degrees ( When the angle is viewed in the right rotation direction in this embodiment, the center of the seal ring (29) is eccentric toward a range between 270 degrees and 360 degrees.

  With the above configuration, when the refrigerant compressed in the cylinder chambers (C1, C2) of the compression mechanism (20) is discharged to the high-pressure space (S2), the pressure of the refrigerant is changed to the drive shaft (33) and the bearing portion (17a ) Acts on the lower surface of the cylinder-side end plate (26A) constituting the first facing portion (61). The pressure of the lubricating oil in the casing (10) also acts on the first facing portion (61). As a result, an upward axial pressing force acts on the cylinder side end plate (26A). Here, since the seal ring (29) is arranged eccentrically from the center of the cylinder (21) and the center of the drive shaft (33), this axial pressing force is also applied to the cylinder (21 ) Acts at an eccentric position from the center. That is, in the pressing mechanism (60), the position eccentric from the center of the cylinder side end plate (26A) of the cylinder (21) is the center of action of the axial pressing force.

  Furthermore, the rotary compressor (1) of Embodiment 1 is provided with a seal mechanism that reduces the axial gap between the cylinder (21) and the annular piston (22) and suppresses fluid leakage in the gap. ing. Specifically, the sealing mechanism is an annular first tip seal provided between the upper end surface (axial end surface) of the outer cylinder (24) and the lower surface of the piston side end plate (26B) (first axial clearance). (71) and an annular second tip seal (72) provided between the upper end surface (axial end surface) of the inner cylinder (25) and the lower surface of the piston side end plate (26B) (first axial clearance) And. Further, the sealing mechanism includes a third tip seal (73) provided between the lower end surface (axial end surface) of the annular piston (22) and the upper surface of the cylinder side end plate (26A) (second axial clearance). I have.

-Driving action-
Next, the operation of the rotary compressor (1) will be described with reference to FIG.

  When the electric motor (30) is started, the rotation of the rotor (32) is transmitted to the outer cylinder (24) and the inner cylinder (25) of the compression mechanism (20) via the drive shaft (33). As a result, the blade (23) reciprocates (advances and retreats) between the swinging bushes (27A, 27B), and the blade (23) and the swinging bushes (27A, 27B) are integrated, Swing operation is performed on the annular piston (22). Then, the outer cylinder (24) and the inner cylinder (25) revolve while swinging with respect to the annular piston (22), and the compression mechanism (20) performs a predetermined compression operation.

  Here, in the outer cylinder chamber (C1), the cylinder (21) revolves clockwise from the state shown in FIG. 3D (the low-pressure chamber (C1-Lp) becomes almost the minimum volume). The refrigerant is sucked into the low pressure chamber (C1-Lp) from the suction port (41). At the same time, the refrigerant is sucked into the low pressure chamber (C1-Lp) through the through hole (43) from the suction space (42) communicating with the suction port (41). When the cylinder (21) revolves in the order of (A), (B) and (C) in FIG. 3 and enters the state of (D) in FIG. 3 again, the refrigerant flows into the low pressure chamber (C1-Lp). Inhalation is complete.

  Here, the low-pressure chamber (C1-Lp) becomes a high-pressure chamber (C1-Hp) in which the refrigerant is compressed, and a new low-pressure chamber (C1-Lp) is formed across the blade (23). When the cylinder (21) further rotates in this state, the suction of the refrigerant is repeated in the newly formed low pressure chamber (C1-Lp), while the volume of the high pressure chamber (C1-Hp) decreases, and the high pressure chamber (C1-Hp) C1-Hp) compresses the refrigerant. When the pressure in the high-pressure chamber (C1-Hp) reaches a predetermined value and the pressure difference with the discharge space (49) reaches a set value, the high-pressure refrigerant in the high-pressure chamber (C1-Hp) causes the discharge valve (47) Opens, and the high-pressure refrigerant flows out from the discharge space (49) through the discharge passage (49a) to the high-pressure space (S2).

  In the inner cylinder chamber (C2), the cylinder (21) revolves clockwise from the state shown in FIG. 3B (the state where the volume of the low-pressure chamber (C2-Lp) is almost minimized). The refrigerant is sucked into the low pressure chamber (C2-Lp) from the port (41). At the same time, the refrigerant is sucked into the low pressure chamber (C2-Lp) through the through hole (44) from the suction space (42) communicating with the suction port (41). When the cylinder (21) revolves in the order of (C), (D) and (A) in FIG. 3 and enters the state of (B) in FIG. 3 again, the refrigerant flows into the low pressure chamber (C2-Lp). Inhalation is complete.

  Here, the low-pressure chamber (C2-Lp) becomes a high-pressure chamber (C2-Hp) in which the refrigerant is compressed, and a new low-pressure chamber (C2-Lp) is formed across the blade (23). When the cylinder (21) further rotates in this state, the suction of the refrigerant is repeated in the newly formed low pressure chamber (C2-Lp), while the volume of the high pressure chamber (C2-Hp) decreases, and the high pressure chamber (C2-Hp) C2-Hp) compresses the refrigerant. When the pressure in the high pressure chamber (C2-Hp) reaches a predetermined value and the differential pressure with respect to the discharge space (49) reaches a set value, the high pressure refrigerant in the high pressure chamber (C2-Hp) causes the discharge valve (48). Opens, and the high-pressure refrigerant flows out from the discharge space (49) through the discharge passage (49a) to the high-pressure space (S2).

  The high-pressure refrigerant compressed in the outer cylinder chamber (C1) and the inner cylinder chamber (C2) and flowing into the high-pressure space (S2) in this way is discharged from the discharge pipe (15) and is condensed and expanded in the refrigerant circuit. And after the evaporating stroke, the air is again sucked into the rotary compressor (1).

-Operation of the pressing mechanism-
Next, the operation of the pressing mechanism (60), which is a feature of the present invention, will be described with reference to FIG.

  During the compression operation of the rotary compressor (1) described above, if the refrigerant becomes high pressure in the cylinder chamber (C1, C2), the pressure of the high-pressure refrigerant becomes the axial thrust load (PT) (the cylinder side end plate ( 26A). Here, if this thrust load (PT) increases or the point of action of the thrust load (PT) moves away from the drive shaft (33), a rollover moment due to the thrust load (PT) is generated, and the eccentric rotating body There is a possibility that the cylinder (21) is overturned.

  For this reason, in the rotary compressor (1) of this embodiment, the overturning moment is reduced by applying an axial pressing force against the thrust load (PT).

  Specifically, when the cylinder (21) is in the state shown in FIG. 3 (A), the refrigerant in the high pressure chamber (C1-Hp) of the outer cylinder chamber (C1) is at a high pressure, so the thrust load (PT) is 21) Acts closer to the high-pressure chamber (C1-Hp) than the center. On the other hand, as described above, by disposing the seal ring (29) between the cylinder side end plate (26A) and the lower housing (17), the pressure of the high-pressure refrigerant is changed to the cylinder side end plate in the first facing portion (61). Acting on the lower surface of (26A), as a result, an axial pressing force (P) pressing the cylinder side end plate (26A) upward against the piston (22) is generated against the thrust load (PT). Here, the seal ring (29) is arranged eccentric from the center of the cylinder (21) toward the discharge port (45, 46), and the axial pressing force (P) obtained by the pressing mechanism (60) is also the cylinder. Acts closer to the discharge port (45, 46) from the center of (21). Therefore, the point of application of the thrust load (PT) and the point of application of the axial pressing force (P) are easily matched in the radial direction, and the rollover moment is effectively reduced.

  When the cylinder (21) is in the state shown in FIG. 3B, the refrigerant in the high pressure chamber (C1-Hp) of the outer cylinder chamber (C1) or the high pressure chamber (C2-Hp) of the inner cylinder chamber (C2) High pressure is applied, and the thrust load (PT) also acts closer to the high pressure chamber (C1-Hp) from the center of the cylinder (21). Even in this state, since the axial pressing force (PT) of the pressing mechanism (60) acts closer to the discharge port (45, 46) from the center of the cylinder (21), the operating point of the thrust load (PT) The point of application of the axial pressing force (P) easily matches in the radial direction, and the rollover moment is effectively reduced.

  Further, when the cylinder (21) is in the state shown in FIGS. 3C and 3D, the refrigerant in the high pressure chamber (C2-Hp) of the inner cylinder chamber (C2) becomes high pressure, and the thrust load (PT) is 21) Acts from the center to the high pressure chamber (C2-Hp). Even in this state, since the axial pressing force (P) acts closer to the discharge port (45, 46) from the center of the cylinder (21), the operating point of the thrust load (PT) and the axial pressing force (P ) Is easily matched in the radial direction, and the rollover moment is effectively reduced.

-Effect of Embodiment 1-
In the first embodiment, the following effects are exhibited.

  In the present embodiment, an axial pressing force (P) against the cylinder side end plate (26A) obtained by the pressing mechanism (60) is applied to the cylinder (C1, C2) where the thrust load (PT) is likely to act. It is made to act on the position near the discharge port (45, 46) from the center of 21). For this reason, the point of action of the thrust load (PT) and the axial pressing force (P) can be brought close to each other, and the rollover moment can be effectively reduced.

  Here, the pressing mechanism (60) can be easily configured by disposing the seal ring (29) between the cylinder side end plate (26A) and the lower housing (17). That is, the above-described effect of reducing the overturning moment can be obtained with a simple structure.

  Further, the cylinder mechanism end plate (26A) and the piston end panel (26B) are brought close to each other in the axial direction by the pressing mechanism (60), so that the first axial direction between the cylinder (21) and the piston (22) is achieved. The gap and the second axial gap can be reduced, and refrigerant leakage in the axial gap can be suppressed. Therefore, the compression efficiency of this rotary compressor can be improved.

  In Embodiment 1, a plurality of tip seals (71, 72, 73) are arranged in the first axial gap and the second axial gap between the cylinder (21) and the piston (22). For this reason, the leakage of the fluid in the axial gap between the cylinder (21) and the piston (22) can be further suppressed, and the compression efficiency can be further improved.

-Modification 1 of Embodiment 1-
Next, Modification 1 of Embodiment 1 will be described. This modified example 1 is different from the above-described first embodiment in the position where the seal ring (29) is provided. Specifically, the seal ring (29) of the first embodiment is fitted and arranged in an annular groove (17b) formed in the lower housing (17), whereas the seal ring (29) of this modified example is As shown in FIG. 4, it is fitted and arranged in an annular groove (17b) formed in the lower surface of the cylinder side end plate (26A). The seal ring (29) is arranged eccentrically from the center of the cylinder (21) toward the discharge port (45, 46), as in the first embodiment.

  Also in this modified example 1, as shown in FIGS. 4A to 4D, the axial pressing force (P) obtained by the pressing mechanism (60) is shifted in the radial direction with respect to the thrust load (PT). It is difficult to effectively reduce the rollover moment.

-Modification 2 of Embodiment 1
Next, a second modification of the first embodiment will be described. This modification 2 differs in the structure of the pressing mechanism (60) from Embodiment 1 mentioned above. Specifically, in Modification 2, a slit (63) is used as the pressing mechanism (60).

  As shown in FIG. 5, in Modification 2, a slit (63) is formed on the lower surface of the cylinder side end plate (26A). The slit (63) is formed eccentric from the center of the cylinder (21) toward the discharge port (45, 46). Here, when the pressure of the high-pressure refrigerant acts on the slit (63), a pressure gradient is generated, and the cylinder side end plate (26A) is closer to the discharge port (45, 46) from the center of the cylinder (21) ( An axial pressing force eccentric to the left side in FIG. 5 acts. Therefore, also in this modified example 2, as in the first embodiment described above, the point of action of the thrust load (PT) and the point of action of the axial pressing force (P) in the cylinder side end plate (26A) can be brought close to each other. The rollover moment can be effectively reduced.

  Further, the slit (63) can be easily formed by providing a step in the cylinder side end plate (26A). For example, when the cylinder (21) and the cylinder side end plate (26A) are integrally formed by sintering or forging. In addition, the slit (63) can be easily formed.

-Modification 3 of Embodiment 1-
Next, a third modification of the first embodiment will be described. This modified example 3 is different from the above-described first and second modified examples in the configuration of the pressing mechanism (60). Specifically, in the third modification, a through hole (64) and a groove (65) formed in the cylinder side end plate (26A) are used as the pressing mechanism (60).

  In the third modification, two through holes (64) and two grooves (65) as shown in FIG. 6 are formed in the cylinder side end plate (26A). Specifically, the through hole (64) includes an outer through hole (64a) communicating with the outer cylinder chamber (C1) and an inner through hole (64b) communicating with the inner cylinder chamber (C2). On the other hand, the groove (65) includes an outer groove (65a) communicating with the outer through hole (64a) and an inner groove (65b) communicating with the inner through hole (64b). Each groove portion (65) and each through hole (64b) are formed eccentric from the center of the cylinder (21) toward the discharge port (45, 46).

  In the above configuration, when the refrigerant is compressed in the cylinder chambers (C1, C2), the high-pressure refrigerant flows out to the groove portions (65) through the through holes (64). Here, when the refrigerant flows out into each groove (65), the pressure of the refrigerant acts on each groove (65). As described above, in the third modification, a part of the refrigerant compressed in the cylinder chambers (C1, C2) is caused to flow into the groove (65), and the cylinder side end plate (26A) is removed by using the pressure of the refrigerant. An axial pressing force pressing upward is obtained. At this time, since the axial pressing force (P) acts closer to the discharge port (45, 46) from the center of the cylinder (21), the rollover moment can be effectively reduced.

  Moreover, in the modification 3, the pressure of the refrigerant | coolant compressed within the cylinder chamber (C1, C2) is utilized as a pressing mechanism (60). For this reason, when the pressure in the cylinder chamber (C1, C2) increases and the thrust load (PT) increases, the axial pressing force (P) acting on the groove (65) can also be increased. When the thrust load (PT) decreases, the axial pressing force (P) can be decreased. Therefore, it is possible to suppress an increase in mechanical loss of the eccentric rotating body due to the excess axial pressing force (P), and it is possible to effectively reduce the overturning moment.

  Furthermore, in this modification 3, the opening degree of this upper opening can be adjusted by closing the upper opening of the through hole (64) with the lower end of the piston (22) according to the revolution position of the cylinder (21). . In this case, for example, when the pressure in the cylinder chamber (C1, C2) increases and the pressure acting on the groove (65) becomes excessive, the opening degree of the upper opening of the through hole (64) is reduced, and this The pressure can be reduced. On the other hand, for example, when the pressure in the cylinder chamber (C1, C2) decreases and the pressure acting on the groove (65) is insufficient, the opening degree of the upper opening of the through hole (64) is increased and this pressure is increased. be able to. Thus, the shaft acting on the groove (65) by balancing the pressure in the cylinder chamber (C1, C2), which changes according to the revolution position of the cylinder (21), and the opening of the through hole (64). The direction pressing force (P) can be adjusted optimally.

<< Embodiment 2 of the Invention >>
In the second embodiment of the present invention, the first embodiment is configured to perform eccentric rotational movement using the cylinder (21) as an eccentric rotating body, while the annular piston (22) is configured to perform eccentric rotational movement using the eccentric rotating body. It is.

  In this Embodiment 2, as shown in FIG. 7, the compression mechanism (20) is arrange | positioned at the upper part in a casing (10) similarly to Embodiment 1. FIG. The compression mechanism (20) is configured between the upper housing (16) and the lower housing (17) as in the first embodiment.

  On the other hand, unlike the first embodiment, the upper housing (16) is provided with an outer cylinder (24) and an inner cylinder (25). The outer cylinder (24) and the inner cylinder (25) are integrated with the upper housing (16) to constitute a cylinder (21). A cylinder side end plate (26A) is integrally formed at the upper ends of the outer cylinder (24) and the inner cylinder (25).

  An annular piston (22) is held between the upper housing (16) and the lower housing (17). A piston end plate (26B) is integrally formed at the lower end of the annular piston (22). The piston side end plate (26B) is provided with a hub (26a) that is slidably fitted to the eccentric portion (33a) of the drive shaft (33). Therefore, in this configuration, when the drive shaft (33) rotates, the annular piston (22) performs an eccentric rotational motion in the cylinder chambers (C1, C2). The blade (23) is integrated with the cylinder (21) as in the above embodiments.

  The upper housing (16) has a suction port (41) communicating with the outer cylinder chamber (C1) and the inner cylinder chamber (C2) from the low pressure space (S1) above the compression mechanism (20) in the casing (10). The discharge port (45) of the outer cylinder chamber (C1) and the discharge port (46) of the inner cylinder chamber (C2) are formed. A suction space (42) communicating with the suction port (41) is formed between the hub (26a) and the inner cylinder (25). A through hole (44) is formed in the inner cylinder (25) with an annular piston. A through hole (43) is formed in (22).

  A cover plate (18) is provided above the compression mechanism (20), and a discharge space (49) is formed between the upper housing (16) and the cover plate (18). The discharge space (49) communicates with the high-pressure space (S2) below the compression mechanism (20) via a discharge passage (49a) formed in the upper housing (16) and the lower housing (17). .

  In the configuration of the second embodiment, the seal ring (29) is disposed between the piston side end plate (26B) and the lower housing (17). The seal ring (29) is arranged eccentric from the center of the annular piston (22), which is an eccentric rotating body, toward the discharge port (45, 46). The pressing mechanism (60) is configured to apply an axial pressing force to a position eccentric to the discharge port (45, 46) from the center of the annular piston (22) in the piston side end plate (26B). .

  In the second embodiment, even when the annular piston (22) revolves in the order of FIGS. 8 (A) to (D), thrust generated eccentrically from the center of the annular piston (22) toward the discharge port (45, 46). The load (PT) easily matches the axial pressing force (P) generated by the pressing mechanism (60), and the rollover moment for the annular piston (22) can be effectively reduced.

  In FIG. 7, the seal ring (29) is provided on the lower housing (17), whereas in FIG. 8, as an example, a seal ring (29) is provided on the piston side end plate (26B). Although shown, the operation of the pressing mechanism (60) is generally the same.

<< Embodiment 3 of the Invention >>
In the third embodiment of the present invention, the positions of the low pressure space (S1) and the high pressure space (S2) partitioned by the compression mechanism (20) in the casing (10) are upside down from the first and second embodiments. It is what.

  Specifically, in the third embodiment, as shown in FIG. 9, the suction pipe (14) passes through the body (11), and the discharge pipe (15) passes through the upper end plate (12). The suction pipe (14) communicates with the low pressure space (S1) formed on the lower side of the compression mechanism (20), while the discharge pipe (15) is formed on the upper side of the compression mechanism (20). It communicates with the high-pressure space (S2).

  The low pressure space (S1) communicates with a suction space (42) formed from the lower housing (17) to the upper housing (16). The suction space (42) communicates with the cylinder chamber (C1, C2) through the through hole (43, 44) of the outer cylinder (24) and the piston (22) at the axially intermediate portion. Furthermore, the upper end of the suction space (42) communicates with the suction port (41) formed in the upper housing (16). The suction port (41) communicates with the cylinder chambers (C1, C2) as in the first and second embodiments. On the other hand, the high pressure space (S2) communicates with the discharge space (49) through a discharge passage (not shown).

  In the third embodiment, the high pressure introduction passageway (66) is formed across the upper housing (16) and the annular piston (22). The high pressure introduction passage (66) is formed such that its upper end opening is interposed between the two discharge valves (47, 48), and its lower end opening extends in the axial direction to the lower end of the annular piston (22). The cylinder (21) is formed with a through hole (64) communicating with the lower end opening of the high-pressure introduction passage (66). The through hole (64) extends in the axial direction up to a facing portion between the cylinder side end plate (26A) and the lower housing (17). Furthermore, two seal rings (29) are provided at the lower end of the through hole (64). These two seal rings (29) partition the facing portion between the cylinder side end plate (26A) and the lower housing (17) into three facing portions. An annular facing portion sandwiched between two seal rings (29) of the facing portions constitutes a first facing portion (61), and the first facing portion (61) and the through hole (64) communicate with each other. ing.

  With the above configuration, the high-pressure refrigerant compressed by the compression mechanism (20) and discharged into the discharge space (49) passes through the first opposing portion (61) via the high-pressure introduction passage (66) and the through hole (64). ). As a result, the pressure of the high-pressure refrigerant acts on the cylinder side end plate (26A) in the first facing portion (61). Here, the seal ring (29) is arranged eccentric from the center of the cylinder (21) toward the discharge port (45, 46). For this reason, the upward axial pressing force acting on the cylinder side end plate (26A) also acts eccentrically from the center of the cylinder (21) toward the discharge port (45, 46). Therefore, as described above, the rollover moment due to the thrust load can be effectively reduced.

  The seal ring (29) constitutes a seal mechanism that reduces the axial clearance between the cylinder (21) and the annular piston (22) by pressing the cylinder (21) toward the annular piston (22) in the axial direction. The refrigerant leakage in the cylinder chambers (C1, C2) can be suppressed.

-Modification of Embodiment 3-
Next, a modification of the third embodiment will be described with reference to FIG. In this modification, the low-pressure space (S1) is formed below the compression mechanism (20) and the high-pressure space (S2) is formed above the compression mechanism (10) as in the third embodiment. The structure of the housing (16) is different.

  In the upper housing (16) of the third modification, the discharge space (49) is formed over a wider range in the radial direction than in the third embodiment. Further, the discharge passage (49a) for communicating the high pressure space (S2) and the discharge space (49) is formed substantially coaxially with the drive shaft (33).

  Furthermore, the upper housing (16) is not fixed to the inner wall of the body (10), but is locked to a plurality of pins (67) provided near the outer periphery of the upper surface of the lower housing (17). Is retained. Further, in this modification, a tip seal (71) is provided between the lower end surface of the annular piston (22) and the upper surface of the cylinder side end plate (26A).

  With the above configuration, the pressure of the high-pressure refrigerant in the high-pressure space (S2) is applied to the wall surface of the upper housing (16) facing the discharge space (49), so that the upper housing (16) and the annular piston (22) are cylinders. (21) A seal mechanism can be configured to be pressed in the axial direction toward the side. Therefore, the axial clearance between the cylinder (21) and the annular piston (22) can be reduced.

  Also in this modification, for example, in the same manner as Modification 3 of Embodiment 1, by forming the through hole (64) and the groove (65) in the cylinder (22), the inside of the cylinder chamber (C1, C2) The pressing mechanism (60) can be configured by causing the high-pressure refrigerant to act on the groove (65). Also in this case, the overturning moment in the cylinder (21) can be reduced by the pressing mechanism (60).

<< Other Embodiments >>
The present invention may be configured as follows with respect to the above embodiment.

  In the first embodiment, the center of the seal ring (29) provided in the lower housing (17) is eccentrically arranged near the discharge port (45, 46) from the center of the cylinder (21). However, the center of the seal ring (29) may be arranged eccentrically from the center of the lower housing (17) (center of the drive shaft (33)) toward the discharge port (45, 46). Also in this case, the center of the axial pressing force can be applied closer to the discharge port (45, 46), and the point of action between the thrust load (PT) and the axial pressing force (P) can be brought closer. Therefore, the rollover moment can be reduced.

  In the above embodiment, the compression mechanism (60) for applying an axial pressing force to the cylinder side end plate (26A) or the piston side end plate (26B) is provided with two cylinder chambers (C1, C2). It is applied to the machine (1). However, the pressing mechanism (60) can also be applied to other rotary compressors (1).

  For example, the rotary compressor (1) shown in FIG. 11 includes a cylinder (21) having a cylinder chamber (C) having a circular cross-sectional shape perpendicular to the axis, and a circular piston (22) disposed in the cylinder chamber (C). And. The cylinder chamber (C) is divided into a first chamber (C-Hp) and a second chamber (C-Lp) by a blade (not shown). Further, a cylinder side end plate (26A) facing the inside of the cylinder chamber (C) is formed at the upper end portion of the cylinder (21), and the lower end portion of the piston (22) is connected to the inside of the cylinder chamber (C). A piston side end plate (26B) partially facing is formed.

  Even in the above configuration, for example, by decentering the axial pressing force obtained by providing the seal ring (29) from the center of the piston (22), the operating point of the thrust load and the axial pressing force can be changed in the radial direction. The shift can be suppressed and the rollover moment can be effectively reduced.

  In the above embodiment, the axial pressing force is obtained by the high pressure in the high pressure space (S2) or the pressure (intermediate pressure) in the cylinder chambers (C1, C2). However, for example, the high pressure in the high pressure space (S2) is introduced into the low pressure space (S1) via a pressure regulating valve, etc., and the axial pressing force is obtained by the pressure in the low pressure space (S1) that has become the intermediate pressure. Good.

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.

  As described above, the present invention is particularly useful in a rotary compressor in which an overturning moment easily acts on an eccentric rotating body such as a piston or a cylinder.

1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1. FIG. It is a cross-sectional view of a compression mechanism. It is a cross-sectional view showing the operation of the compression mechanism. FIG. 6 is a cross-sectional view illustrating the operation of the compression mechanism of the rotary compressor according to the first modification of the first embodiment. It is a longitudinal cross-sectional view of the compression mechanism of the rotary compressor which concerns on the modification 2 of Embodiment 1. FIG. It is a longitudinal cross-sectional view of the compression mechanism of the rotary compressor which concerns on the modification 3 of Embodiment 1. FIG. 4 is a longitudinal sectional view of a rotary compressor according to Embodiment 2. FIG. It is a cross-sectional view showing the operation of the compression mechanism. It is a longitudinal cross-sectional view of the rotary compressor which concerns on Embodiment 3. FIG. 6 is a longitudinal sectional view of a rotary compressor according to a modification of the third embodiment. It is a longitudinal cross-sectional view which shows the compression mechanism of the rotary compressor of other embodiment. It is a partial longitudinal cross-sectional view of the rotary compressor which concerns on a prior art. It is XIII-XIII sectional drawing of FIG. It is a cross-sectional view showing the operation of the compression mechanism.

Explanation of symbols

1 Compressor
10 Casing
17 Lower housing (support plate)
20 Compression mechanism
21 cylinders
22 Piston
23 blades
26A End plate on cylinder side
26B Piston side end plate
27 Swing bush
29 Seal ring
33 Drive shaft
C1 Cylinder chamber (outer cylinder chamber)
C2 Cylinder chamber (inner cylinder chamber)
C1-Hp 1st chamber (high pressure chamber)
C2-Hp 1st chamber (high pressure chamber)
C1-Lp 2nd chamber (suction chamber)
C2-Lp 2nd chamber (suction chamber)
45, 46 Discharge port
60 Pushing mechanism
61 First counter part
71 Tip seal
72 Tip seal
73 Tip seal

Claims (11)

A cylinder (21) having a cylinder chamber (C) (C1, C2), a piston (22) eccentrically stored in the cylinder chamber (C) (C1, C2) and the cylinder It is arranged in the chamber (C) (C1, C2), and the cylinder chamber (C) (C1, C2) is divided into the first chamber (C-Hp) (C1-Hp, C2-Hp) and the second chamber (C-Lp ) (C1-Lp, C2-Lp) and a blade (23) partitioned into at least one of the cylinder (21) and the piston (22) as an eccentric rotating body (21, 22) A compression mechanism (20) for movement;
A drive shaft (33) for driving the compression mechanism (20);
Cylinder side end plate (26A) provided on one axial end of the cylinder chamber (C) (C1, C2) and facing the axial end surface of the piston (22), and the cylinder chamber (C) (C1, C2) A pressing mechanism (60) provided on the other axial end side of the piston and facing the piston end plate (26B) facing the axial end surface of the cylinder (21) in the axial direction of the drive shaft (33);
A rotary compressor comprising a casing (10) for housing the compression mechanism (20), the drive shaft (33), and the pressing mechanism (60),
The pressing mechanism (60) is the center of action of the axial pressing force at a position eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22) and from the center of the drive shaft (33). It is configured so as to be,
The compression mechanism (20) has discharge ports (45, 46) for discharging the fluid compressed in the cylinder chambers (C1, C2) to the outside of the compression mechanism (20).
The pressing mechanism (60) is located outside the locus whose radius is the amount of eccentricity of the eccentric rotating body (21, 22) with respect to the center of the drive shaft (33), and the end plate of the eccentric rotating body (21, 22) ( A rotary compressor characterized in that the position eccentric from the center of 26A, 26B toward the discharge port (45, 46) is the center of action of the axial pressing force . The rotary compressor according to claim 1, wherein
The cylinder chamber (C) has a cross-sectional shape perpendicular to the axis formed in a circle,
A rotary compressor characterized in that the piston (22) is constituted by a circular piston (22) disposed in the cylinder chamber (C). The rotary compressor according to claim 1, wherein
The cylinder chamber (C1, C2) has a cross-sectional shape perpendicular to the axis,
A piston (22) is disposed in the cylinder chamber (C1, C2), and an annular piston (22) that divides the cylinder chamber (C1, C2) into an outer cylinder chamber (C1) and an inner cylinder chamber (C2). A rotary compressor characterized in that it is configured. The rotary compressor according to claim 3,
The piston (22) is formed in a C-shape in which a part of the ring is divided,
A swinging bush (27) having a blade groove (28) for holding the blade (23) so as to be able to advance and retreat is swingably held at the dividing portion of the piston (22),
The blade (23) is configured to extend through the blade groove (28) from the inner peripheral wall surface to the outer peripheral wall surface of the annular cylinder chamber (C1, C2). Features a rotary compressor. The rotary compressor according to any one of claims 1 to 4,
In the casing (10), a support plate (17) is arranged along the opposite surface of the end face (26A, 26B) of the eccentric rotor (21, 22) on the cylinder chamber (C1, C2) side,
On one end of the end plate (26A, 26B) and the support plate (17) of the eccentric rotating body (21, 22), the opposite portion (61, 62) between the end plate (26A, 26B) and the support plate (17) is provided. A seal ring (29) that is divided into a first facing portion (61) and a second facing portion (62) separated inward and outward in the direction is provided at a position eccentric from the center of the eccentric rotating body (21, 22);
The pressing mechanism (60) is configured to apply the pressure of the fluid discharged to the outside of the compression mechanism (20) to the first facing portion (61) of the end plate (26A, 26B). Rotary compressor to do. The rotary compressor according to claim 5 ,
The rotary compressor characterized in that the seal ring (29) is fitted in an annular groove (17b) formed in either the eccentric rotating body (21, 22) or the support plate (17). . The rotary compressor according to any one of claims 1 to 4 ,
A slit (63) is formed at the position opposite to the cylinder chamber (C1, C2) side surface of the end plate (26A) of the eccentric rotating body (21) and eccentric from the center of the eccentric rotating body (21).
The rotary compressor characterized in that the pressing mechanism (60) is configured to cause the pressure of the fluid discharged to the outside of the compression mechanism (20) to act on the slit (63) . The rotary compressor according to any one of claims 1 to 4 ,
A groove (65) formed on the end surface (26A) of the eccentric rotating body (21) opposite to the surface on the cylinder chamber (C1, C2) side and at a position eccentric from the center of the eccentric rotating body (21) ; A through hole (64) formed in the end plate (26A) so as to communicate the groove (65) and the cylinder chamber (C1, C2);
The pressing mechanism (60) introduces a part of the fluid compressed in the cylinder chamber (C1, C2) to the groove (65) through the through hole (64), and applies the pressure of the fluid to the groove (65). It is comprised so that it may act, The rotary compressor characterized by the above-mentioned. The rotary compressor according to any one of claims 1 to 8 ,
The first axial clearance between the axial end surface of the cylinder (21) and the piston end plate (26B) and the second axial clearance between the axial end surface of the piston (22) and the cylinder end plate (26A) A rotary compressor comprising a seal mechanism (71, 72, 73) for suppressing leakage of fluid in at least one of them. The rotary compressor according to claim 9 ,
The rotary compressor is characterized in that the seal mechanism is constituted by tip seals (71, 72, 73) provided in at least one of the first axial gap and the second axial gap . A cylinder (21) having a cylinder chamber (C) (C1, C2), a piston (22) eccentrically stored in the cylinder chamber (C) (C1, C2) and the cylinder It is arranged in the chamber (C) (C1, C2), and the cylinder chamber (C) (C1, C2) is divided into the first chamber (C-Hp) (C1-Hp, C2-Hp) and the second chamber (C-Lp ) (C1-Lp, C2-Lp) and a blade (23) partitioned into at least one of the cylinder (21) and the piston (22) as an eccentric rotating body (21, 22) A compression mechanism (20) for movement;
A drive shaft (33) for driving the compression mechanism (20);
Cylinder side end plate (26A) provided on one axial end of the cylinder chamber (C) (C1, C2) and facing the axial end surface of the piston (22), and the cylinder chamber (C) (C1, C2) A pressing mechanism (60) provided on the other axial end side of the piston and facing the piston end plate (26B) facing the axial end surface of the cylinder (21) in the axial direction of the drive shaft (33);
A rotary compressor comprising a casing (10) for housing the compression mechanism (20), the drive shaft (33), and the pressing mechanism (60),
The pressing mechanism (60) is the center of action of the axial pressing force at a position eccentric from the center of the end plate (26A, 26B) of the eccentric rotating body (21, 22) and from the center of the drive shaft (33). Configured to be
A slit (63) is formed at the position opposite to the cylinder chamber (C1, C2) side surface of the end plate (26A) of the eccentric rotating body (21) and eccentric from the center of the eccentric rotating body (21).
The rotary compressor characterized in that the pressing mechanism (60) is configured to cause the pressure of the fluid discharged to the outside of the compression mechanism (20) to act on the slit (63) .

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