JP4609496B2 - Rotary fluid machine - Google Patents

Description

  The present invention relates to a rotary fluid machine, and in particular, a rotary type in which eccentric rotary piston mechanisms having a cylinder having an annular cylinder chamber and an annular piston housed eccentrically in the cylinder chamber are arranged in two stages. The present invention relates to a fluid machine.

  2. Description of the Related Art Conventionally, a rotary fluid machine including an eccentric rotary piston mechanism having a cylinder having a cylinder chamber and a piston housed eccentrically in the cylinder chamber is known. The eccentric rotary piston mechanism is configured such that the volume of the cylinder chamber fluctuates periodically by rotating the piston eccentrically with respect to the cylinder chamber. The eccentric rotary piston mechanism is configured to suck fluid gas into the cylinder chamber and compress the sucked fluid gas to the outside of the cylinder chamber in accordance with the volume change of the cylinder chamber. ing.

  Patent Document 1 discloses a rotary compressor as this type of rotary fluid machine. In the eccentric rotary piston mechanism of the rotary compressor, the cylinder chamber constitutes a compression chamber, and the compression chamber and the piston are each formed in an annular shape. The annular piston is stored eccentrically in the cylinder chamber so as to divide the annular compression chamber into an outer compression chamber and an inner compression chamber, and a cylinder having an annular cylinder chamber with respect to the annular piston is provided. It is configured to rotate eccentrically.

  Specifically, in the outer compression chamber and the inner compression chamber, the volume of the outer compression chamber and the inner compression chamber is increased with the rotation of the cylinder, whereby the refrigerant is sucked into each compression chamber, and then the volume of each compression chamber. As the pressure decreases, the refrigerant pressure gradually increases. When the refrigerant pressure reaches a predetermined pressure, the discharge valve that closed each compression chamber is opened, and the refrigerant is discharged from the compression chamber. As described above, the volume of each compression chamber periodically changes with the rotation of the annular cylinder, and the refrigerant pressure in each compression chamber also changes periodically with the periodic fluctuation of the volume of each compression chamber. If the change in the refrigerant pressure in the compression chamber is large, the output torque fluctuation of the drive shaft also increases, and in some cases, the vibration and noise of the rotary compressor increase.

  Therefore, in order to suppress fluctuations in the output torque of the drive shaft, Patent Document 2 discloses a rotary compressor (60) in which the eccentric rotary piston mechanisms of Patent Document 1 are arranged in two stages. Specifically, as shown in FIG. 4, the rotary compressor (60) of Patent Document 2 has an upper side with a disc-shaped middle plate (63) having a peripheral edge fixed to the inner wall of the casing (62). Housings (64, 65) are provided on the lower side and the lower side, respectively. The cylinder (66) and the annular piston (67) are housed in the upper space surrounded by the upper housing (65) and the middle plate (63), and are surrounded by the lower housing (64) and the middle plate (63). A cylinder (66) and an annular piston (67) are housed in the lower space.

  Further, the rotary compressor (60) has an inner side formed on the upper side and the lower side, respectively, with the phase of the fluctuation cycle of the volume of the outer compression chamber (68) formed on the upper side and the lower side shifted from each other by 180 degrees. The phase of the fluctuation cycle of the volume of the compression chamber (69) is configured to be shifted from each other by 180 degrees.

According to this configuration, the torque fluctuation of the drive shaft (70) generated with the change of the refrigerant pressure in the upper compression chambers (68, 69) is reduced in the lower compression chambers (68, 69). This can be offset by torque fluctuations of the drive shaft (70) that occur with changes in the refrigerant pressure. Therefore, the torque fluctuation of the drive shaft (70) can be suppressed small as a whole of the rotary compressor (1), and the vibration and noise of the rotary compressor (1) can be reduced.
JP-A-2005-330962 JP 2007-239666 A

  However, when the eccentric rotary piston mechanism is arranged in two upper and lower stages as in the rotary compressor of Patent Document 2, the output torque fluctuation of the drive shaft is suppressed smaller than in the case where the eccentric rotary piston mechanism is one stage. However, since the eccentric rotary piston mechanism is configured in two stages, there is a problem that the structure becomes complicated and the number of parts increases.

  The present invention has been made in view of such a point, and an object of the present invention is to provide an eccentric rotary piston mechanism having a cylinder having an annular cylinder chamber and an annular piston housed eccentrically in the cylinder chamber in two stages. In the rotary fluid machine arranged on top of each other, the number of components is reduced as much as possible while reducing vibration and noise, and the cost of the rotary fluid machine is reduced.

  The first invention includes an eccentric rotary piston mechanism (20) in the casing (10), and a drive mechanism (30) having a drive shaft (33) for driving the eccentric rotary piston mechanism (20), The eccentric rotary piston mechanism (20) includes a cylinder having an annular cylinder chamber (C1, C2, C3, C4), and an annular cylinder chamber (C1, C2, C3, C4) connected to the outer cylinder chamber (C1, An annular piston housed eccentrically in the annular cylinder chamber (C1, C2, C3, C4) so as to be divided into C3) and an inner cylinder chamber (C2, C4); and an outer cylinder chamber (C1, C3); A rotary fluid machine having blades that divide the inner cylinder chamber (C2, C4) into a high-pressure side and a low-pressure side, respectively, and the annular piston compresses fluid by performing eccentric rotational movement with respect to the cylinder Is assumed.

  The cylinder of the rotary fluid machine includes first and second cylinders (21, 21) facing each other in the axial direction, and forms an internal space (S1) between the cylinders (21, 21). Annular cylinder chambers (C1, C2, C3, C4) are fixed on both sides in the axial direction of the internal space (S1), and the annular piston is accommodated in the internal space (S1) and is mutually connected to the shaft. The first and second annular pistons (22, 22) opposed to each other, and one side of each annular piston (22, 22) is attached to the surface of the end plate (22c, 22c), while each annular piston (22 , 22) with the rotating shafts decentering in opposite directions around the axis of the drive shaft (33), the annular pistons (22, 22) are aligned so that the back surfaces of the end plates (22c, 22c) are aligned with each other. ) Is fixed to the drive shaft (33).

  Further, an annular seal member (24) is provided so as to be sandwiched between the end plates (22c, 22c) of both the annular pistons (22, 22), and the inside of the seal member (24) is inside the casing (10). The suction fluid communicates with the high pressure space (S2) where the compressed fluid acts, the outside of the seal member (24) communicates with the internal space (S1), and communicates with the cylinder chambers (C1, C2, C3, C4) Between the port (41) and the internal space (S1), the internal space (S1) is maintained at a pressure higher than the fluid pressure of the suction port (41) and lower than the fluid pressure of the high-pressure space (S2). A back pressure adjusting mechanism (35) is provided.

In addition, each cylinder (21, 21) is provided with a discharge port (45, 46) for communicating each cylinder chamber (C3, C4) on the high-pressure side with the casing (10) . Moreover, 1st invention is a through-passage (38) which penetrates the lubricating oil stored in the lower part in the said casing (10) from the lower end surface of the said drive shaft (33) to the outer peripheral surface of this drive shaft (33). An oil supply means (34) for supplying a sliding surface formed inside the seal member (24) between the end plates (22c, 22c) of the two annular pistons (22, 22) is provided.

  In the first invention, the annular pistons (22, 22) are fixed to the drive shaft (33) so that the back surfaces of the end plates (22c, 22c) of the annular pistons (22, 22) are aligned with each other. As a result, the eccentric rotary piston mechanism (20) can be configured without using the middle plate unlike the conventional case.

  Each annular piston (22, 22) has a drive shaft (33) so that the rotation shaft of each annular piston (22, 22) is eccentric in the opposite direction around the axis of the drive shaft (33). ). As a result, the phases of the fluctuation cycles of the volumes in the outer cylinder chambers (C1, C3) formed on the upper side and the lower side are shifted from each other by 180 degrees, and the volumes in the inner cylinder chambers (C2, C4) formed on the upper side and the lower side. The phases of the fluctuation periods can be shifted from each other by 180 degrees. Therefore, the torque fluctuation of the drive shaft (33) generated in the upper eccentric rotary piston mechanism (20) is canceled by the torque fluctuation of the drive shaft (33) generated in the lower eccentric rotary piston mechanism (20). As a result, the torque fluctuation of the drive shaft (33) can be kept small as the entire rotary fluid machine.

  On the other hand, each annular piston (22, 22) is pressed against each cylinder (21, 21) by the pressure between the end plates (22c, 22c) of the both annular pistons (22, 22). Here, when the high pressure is supplied to the sliding surface, the pressure between the end plates (22c, 22c) also becomes a high pressure state. Therefore, if the pressure between the end plates (22c, 22c) becomes too high, the annular piston (22, 22) may be excessively pressed against the cylinder (21, 21).

  In the first invention, the annular seal member (24) partitions the end plates (22c, 22c) of both annular pistons (22, 22) into an inner side and an outer side of the annular seal member (24). can do. Then, by partitioning the end plates (22c, 22c), only the inner part of the annular seal member (24) can be brought into a high pressure state. That is, the high-pressure region can be made narrower than when no annular seal member (24) is provided. Thereby, it can suppress that an annular piston (22,22) is pressed against a cylinder (21,21) excessively.

  The high-pressure gas in the high-pressure cylinder chambers (C3, C4) is discharged from the discharge port (45, 46) into the casing (10). As a result, the inside of the casing (10) is in a high pressure state. When the inside of the casing (10) is in a high pressure state, the lubricating oil stored in the casing (10) is also in a high pressure state. The high-pressure lubricating oil is supplied to the sliding surface through the oil supply means (34).

  According to a second aspect of the present invention, in the first aspect, the first and second rotation prevention mechanisms (23, 23) for preventing the rotation of the first and second annular pistons (22, 22) include the annular pistons ( 22 and 22) are provided on the surface side of the end plate (22c, 22c).

  In the second invention, since the first and second rotation prevention mechanisms (23, 23) are provided on the surface sides of the end plates (22c, 22c) of the respective annular pistons (22, 22), the rotation prevention mechanism Compared with the case where is provided on the back side of the end plate (22c, 22c), the back sides of the end plate (22c, 22c) can be easily aligned.

  According to a third aspect, in the second aspect, the blade includes a first blade (23) constituting the first rotation prevention mechanism (23) and a second blade (second blade constituting the second rotation prevention mechanism (23)). Each of the annular pistons (22, 22) has a straight part (22d, 22d) continuous with the other part in a part of the circumferential direction, and each of the blades (23, 23) The outer blade portion (23a) that partitions the outer cylinder chamber (C1, C3) and the inner blade portion (23b) that partitions the inner cylinder chamber (C2, C4) are integrally formed, and the outer blade portion (23a) and an inner blade portion (23b) are formed with recesses (23c) that are slidably fitted to the linear portions (22d) of the annular pistons (22, 22). (21, 21) fits the outer blade part (23a, 23a) and inner blade part (23b, 23b) slidably in the cylinder radial direction Blade groove (28) is characterized by being formed respectively that.

  In the third invention, the blades (23, 23) slide in the radial direction with respect to the cylinders (21, 21) by sliding in the blade grooves (28, 28). Movement in a direction perpendicular to the cylinder radial direction is restricted with respect to (21, 21). Then, each annular piston (22, 22) is fitted into the concave portion (23c) of each blade (23, 23) by fitting the linear portion (22d) of each annular piston (22, 22) to each blade (23, 23). 23, 23) and slide in the cylinder radial direction with respect to each cylinder (21, 21).

  Each annular piston (22, 22) slides in the concave portion (23c) of each blade (23, 23) by the linear portion (22d) of each annular piston (22, 22), so that each cylinder ( 21 and 21) is slid in a direction perpendicular to the cylinder radial direction. Thereby, each annular piston (22, 22) can be eccentrically rotated.

  Here, each annular piston (22, 22) slides in a direction perpendicular to the cylinder radial direction with respect to each blade (23, 23), and only moves in the cylinder radial direction with each blade (23, 23). Yes, the displacement of each annular piston (22, 22) in the rotational direction is restricted. Thereby, rotation of each annular piston (22, 22) can be regulated by each blade (23, 23).

  According to the first invention, unlike the prior art, the eccentric rotary piston mechanism (20) can be configured without using a middle plate. Further, the torque fluctuation of the drive shaft (33) generated by the upper eccentric rotary piston mechanism (20) is canceled by the torque fluctuation of the drive shaft (33) generated by the lower eccentric rotary piston mechanism (20). As a result, the torque fluctuation of the drive shaft (33) can be kept small as the entire rotary fluid machine. Therefore, it is possible to reduce the cost of the rotary fluid machine by reducing the middle plate while reducing vibration and noise due to torque fluctuation of the drive shaft (33).

  Further, according to the first invention, unlike the conventional rotary fluid machine, the annular piston (22, 22) is attached to the cylinder (21, 21) while reducing the number of the annular seal members (24). It is possible to suppress excessive pressing. That is, in the conventional case, since the middle plate is provided between the upper and lower movable members, the middle plate is located between the upper surface and the upper movable member, and the lower surface and the lower movable member of the middle plate. It is necessary to provide the annular seal member (24) between each member.

  However, in the rotary fluid machine of the first invention, only one annular seal member (24) may be provided between the end plates (22c, 22c) of both annular pistons (22, 22). Thereby, cost reduction of a rotary fluid machine can be achieved. Further, by setting the inner side of the annular seal member (24) to be small, it is possible to suppress the annular piston (22, 22) from being excessively pressed.

  According to the second invention, the first and second rotation prevention mechanisms (23, 23) are provided on the surface side of the end plate (22c, 22c) of each annular piston (22, 22). Compared with the case where the rotation prevention mechanism is provided on the back side of the end plate (22c, 22c), the back sides of the end plate (22c, 22c) can be easily aligned. Thereby, it becomes easy to delete the middle plate provided in the conventional rotary fluid machine, and the cost of the rotary fluid machine can be reduced.

  According to the third aspect of the invention, the blades (23, 23) provided on the surface side of the end plates (22c, 22c) of the annular pistons (22, 22) are respectively connected to the annular pistons (22, 22). It also serves as a rotation prevention mechanism of 22). Therefore, the back surfaces of the end plates (22c, 22c) can be matched with each other without providing a rotation prevention mechanism. Thereby, it becomes easy to delete the middle plate provided in the conventional rotary fluid machine, and the cost of the rotary fluid machine can be reduced.

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

  As shown in FIG. 1, in the rotary fluid machine according to the embodiment, an electric motor (drive mechanism) (30) and a compression mechanism (eccentric rotary piston mechanism) (20) are housed in a casing (10). It is a rotary compressor (1) configured in a completely sealed type. The rotary compressor (1) is provided, for example, in a refrigerant circuit of an air conditioner, and is used to compress gas refrigerant sucked from an evaporator and discharge it to a condenser.

  The casing (10) includes a barrel (11) formed in a vertically long cylindrical shape, an upper end plate (12) fixed to the upper end of the barrel (11), and a lower end of the barrel (11). And a lower end plate (13) fixed to the airtight container. The upper end plate (12) is provided with a discharge pipe (15) passing through the upper end plate (12). The discharge pipe (15) communicates with the inside of the casing (10), and the inlet thereof opens into a space above the electric motor (30) disposed in the upper part of the casing (10). The body (11) is provided with two suction pipes (14) passing through the body (11). These suction pipes (14) are respectively connected to a compression mechanism (20) disposed in the lower part of the casing (10).

  The rotary compressor (1) is configured such that the refrigerant compressed by the compression mechanism (20) is discharged into the casing (10) (S2) and then passed through the discharge pipe (15) to the casing (10). It is configured to be sent out. Therefore, during the operation of the rotary compressor (1), the inside of the casing (10) becomes a high-pressure space (S2).

  The electric motor (30) includes a stator (31) and a rotor (32). The stator (31) has a cylindrical shape and is fixed to the inner surface of the body (11) of the casing (10). On the other hand, a drive shaft (33) is connected to the rotor (32), and the drive shaft (33) is configured to rotate together with the rotor (32).

  An oil supply passage (through passage) (38) extending from the lower end surface of the drive shaft (33) to the outer peripheral surface is formed inside the drive shaft (33). An oil pump (oil supply means) (34) is provided at the lower end of the drive shaft (33). And by this oil pump (34), the lubricating oil in the reservoir (59) provided at the bottom of the casing (10) is passed through the oil supply passage (38) to each sliding part of the compression mechanism (20), And it supplies to the sliding surface formed between the annular pistons (22) arrange | positioned back to back mentioned later.

  The upper and lower eccentric parts (33b, 63b) in FIG. 1 are provided below the drive shaft (33) so as to be adjacent to each other. These eccentric parts (33b, 63b) are formed to have a larger diameter than the upper and lower parts of the eccentric parts (33b, 63b). The axes of the eccentric portions (33b) are eccentric in opposite directions around the axis of the drive shaft (33).

  The compression mechanism (20) includes two compression units (20a, 20b). These compression parts (20a, 20b) have substantially the same configuration except that the axis of the eccentric part (33b) is eccentric, and these compression parts (20a, 20b) are adjacent to each other in the vertical direction. Has been placed.

  The upper and lower compression parts (20a, 20b) include a cylinder (21) having an annular cylinder chamber (C1, C2, C3, C4) and the annular cylinder chamber (C1, C2, C3, C4). An annular piston (22) eccentrically housed in the annular cylinder chamber (C1, C2, C3, C4) so as to be divided into an outer cylinder chamber (C1, C3) and an inner cylinder chamber (C2, C4); Blades (23) for dividing the outer cylinder chamber (C1, C3) and the inner cylinder chamber (C2, C4) into a high pressure side and a low pressure side, respectively. In each compression section (20a, 20b), the annular piston (22) is configured to perform eccentric rotational movement with respect to the cylinder (21) within the cylinder chamber (C1, C2, C3, C4).

  The upper and lower cylinders (21, 21) each include an outer cylinder part (21a), an inner cylinder part (21b), and a cylinder side end plate (21c). Each cylinder (21) is formed by connecting the end portion of the outer cylinder portion (21a) and the end portion of the inner cylinder portion (21b) with a cylinder side end plate (21c). Further, the drive shaft (33) passes through the central portion of both cylinders (21, 21), and the drive shaft (33) is formed on the inner peripheral surface of the through hole through which the drive shaft (33) passes. Are respectively provided with sliding bearings (16) for rotatably supporting them.

  The upper and lower cylinders (21, 21) end face of the outer cylinder part (21a) of each cylinder (21, 21) so that an internal space (S1) is formed between both cylinders (21, 21). They are fixed in close contact with each other. The outer peripheral surfaces of both cylinders (21, 21) thus fixed are fixed to the inner peripheral surface of the casing (10) by welding or the like. Two annular pistons (22, 22) are accommodated in the internal space (S1).

  These annular pistons (22, 22) are arranged back to back in the vertical direction in FIG. Each annular piston (22, 22) includes an annular piston portion (22a), a bearing portion (22b), and a piston side end plate (22c). Each annular piston (22) is formed by connecting the end portion of the piston portion (22a) and the end portion of the bearing portion (22b) with a piston side end plate (22c).

  The upper and lower annular pistons (22) are fixed to the drive shaft (33) so that the bearing portions (22b) are fitted to the eccentric portions (33b, 63b) of the drive shaft (33). ing. Here, as described above, the upper and lower eccentric parts (33b, 63b) are eccentric in the opposite directions with the axis of both eccentric parts (33b, 63b) centering on the axis of the drive shaft (33). It is formed to do. Therefore, the upper and lower annular pistons (22, 22) fitted to the eccentric parts (33b, 63b) are also centered on the axis of the drive shaft (33). Are eccentric in opposite directions.

  A minute gap is formed between the upper and lower piston side end plates (22c), and a seal ring (24) is provided in the minute gap. The seal ring (24) divides the minute gap into an inner side and an outer side, and the inner side of the seal ring (24) is pressurized via an oil supply passage (38) of the drive shaft (33). It communicates with the space (S2). Here, by supplying lubricating oil from the oil supply passage (38) to the inside of the seal ring (24), the minute gap is in a high pressure state. Then, the pressure inside the seal ring (24) presses the upper annular piston (22) toward the upper cylinder (21), and the lower annular piston (22) toward the lower cylinder (21). Configures the back pressure for pressing.

  On the other hand, the outside of the seal ring (24) communicates with an internal space (S1) formed between both cylinders (21, 21). The pressure in this internal space (S1) is caused by the lubricant that enters beyond the seal ring (24) or the lubricant that leaks from the bearing through the cylinder chamber (C1, C2, C3, C4). Although it rises, it is comprised so that it may not become more than predetermined pressure by the back pressure adjustment mechanism (35) mentioned later.

  The upper and lower blades (23) each have an outer blade portion (23a) that partitions the outer cylinder chamber (C1, C3) and an inner blade portion (23b) that partitions the inner cylinder chamber (C2, C4). A rectangular plate-shaped member formed integrally, and a recess (23c) is formed between the outer blade portion (23a) and the inner blade portion (23b).

  In each compression part (20a, 20b), the cylinder (21) and the annular piston (22) are respectively arranged as shown in FIG. The annular piston (22) is formed continuously without being divided by the piston part (22a), and a part of the piston part (22a) in the circumferential direction is orthogonal to the radial direction passing through the center line of the blade. A straight portion (22d) is formed.

  On the other hand, in the outer cylinder part (21a) and the inner cylinder part (21b) of each cylinder (21, 21), the part corresponding to the straight part (22d) of the piston part (22a) is orthogonal to the radial direction. A straight line portion is formed. A blade groove (28) for slidably fitting the blade (23) fitted to the piston part (22a) is formed in the straight part of both cylinder parts (21a, 21b). It is continuously formed in a straight line along the direction.

 Each of the blades (23) is slidably fitted into the blade groove (28) while the concave portion (23c) is slidably fitted to the linear portion (22d) of the piston portion (22a). Thus, as described above, the outer blade portion (23a) partitions the outer cylinder chamber (C1, C3) into the high pressure side (C1) and the low pressure side (C3), and the inner blade portion (23b) is the inner cylinder chamber. (C2, C4) is divided into a high pressure side (C2) and a low pressure side (C4).

  Moreover, the outer peripheral surface of the inner cylinder part (21b) and the inner peripheral surface of the outer cylinder part (21a) are formed by cylindrical surfaces arranged concentrically with each other. An annular cylinder chamber (C1, C2, C3, C4) as a compression chamber is formed between the inner peripheral surface of the outer cylinder portion (21a) and the outer peripheral surface of the inner cylinder portion (21b). Yes.

  The piston portion (22a) of the annular piston (22) is positioned in the cylinder chamber (C1, C2, C3, C4). That is, the outer peripheral surface of the piston part (22a) is formed with a smaller diameter than the inner peripheral surface of the outer cylinder part (21a), and the inner peripheral surface of the piston part (22a) is smaller than the outer peripheral surface of the inner cylinder part (21b). Is also formed in a large diameter. Thus, an outer cylinder chamber (C1, C3) is formed between the outer peripheral surface of the piston part (22a) and the inner peripheral surface of the outer cylinder part (21a), while the inner peripheral surface of the piston part (22a) Inner cylinder chambers (C2, C4) are formed between the outer peripheral surface of the inner cylinder part (21b).

  Each annular piston (22) and each cylinder (21) are in a state where the outer peripheral surface of the piston portion (22a) and the inner peripheral surface of the outer cylinder portion (21a) are substantially in contact at one point (strictly speaking, In the state where there is a minute gap of micron order, but refrigerant leakage through the minute gap does not matter), the inner peripheral surface of the piston part (22a) and the inner cylinder at a position that is 180 degrees out of phase with the contact point. The outer peripheral surface of the portion (21b) is substantially in contact with one point.

  Each cylinder (21) is formed with a suction port (41) penetrating the outer cylinder portion (21a) in the cylinder radial direction. The suction port (41) has one end opened to the low pressure chamber (C1) of the outer cylinder chamber (C1, C3), and the other end is inserted with a suction pipe (14). Further, the piston part (22a) has a through hole (44) for communicating the low pressure chamber (C1) of the outer cylinder chamber (C1, C3) and the low pressure chamber (C2) of the inner cylinder chamber (C2, C4). Is formed.

  Each cylinder (21) has an outer discharge port (45) and an inner discharge port (46) penetrating the cylinder side end plate (21c) in the thickness direction. The opening end on the annular piston (22) side of the outer discharge port (45) faces the high pressure chamber (C3) of the outer cylinder chamber (C1, C3), and the opening on the annular piston (22) side of the inner discharge port (46) The end faces the high pressure chamber (C4) of the inner cylinder chamber (C2, C4). The outer discharge port (45) and the inner discharge port (46) are each provided with a discharge valve (not shown) including a check valve for opening and closing the port.

  1, the lower cylinder (21) has a communication passage (36) and a check valve (37) provided in the communication passage (36) for opening and closing the communication passage (36). A back pressure adjusting mechanism (35) is provided. The communication path (36) is configured to communicate the internal space (S1) and the suction port (41).

  The check valve (37) has a valve chamber in which a fluid inlet and a fluid outlet are formed, and a ball valve and a coil spring are accommodated in the valve chamber. A valve seat is provided at the fluid inflow port, and a coil spring is attached to urge the ball valve toward the valve seat. When the pressure in the fluid inlet side, that is, in the internal space (S1) becomes larger than the elastic force of the coil spring, the coil spring contracts and the ball valve is separated from the valve seat and the fluid inlet opens. . On the other hand, when the pressure in the internal space (S1) becomes smaller than the elastic force of the coil spring, the coil spring expands, the ball valve is pressed against the valve seat, and the fluid inlet is closed.

  Further, as can be seen from FIG. 1, the upper end surface of the upper inner cylinder part (21b) is in sliding contact with the upper end surface of the upper piston side end plate (22c), and the lower piston side The tip end surface (upper end surface in FIG. 1) of the lower inner cylinder portion (21b) is in sliding contact with the lower end surface of the end plate (22c).

  On the other hand, the top end surface (upper end surface in FIG. 1) of the upper piston portion (22a) is on the upper surface of the cylinder chamber (C1, C2, C3, C4) except for the portion where the blade (23) is fitted. The tip surface (lower end surface in FIG. 1) of the lower piston portion (22a) is in sliding contact with the cylinder chamber (C1, C2, C3, C4) except for the portion where the blade (23) is fitted. It is in sliding contact with the lower surface. The upper surface of the upper blade (23) is in sliding contact with the lower end surface of the upper cylinder end plate (21c), and the lower surface of the lower blade (23) is the upper end surface of the lower cylinder end plate (21c). Is in sliding contact.

  Further, the tip surface (upper end surface in FIG. 1) of the upper bearing portion (22b) is in sliding contact with the flat plate portion inside the upper inner cylinder portion (21b), and the tip surface of the lower bearing portion (22b). The lower end surface of FIG. 1 is in sliding contact with the flat plate portion inside the lower inner cylinder portion (21b).

  In this way, the cylindrical piston chambers (C1, C2, C3, C4) are formed by the sliding contact between the annular piston (22), the cylinders (21, 21), and the blades (23). ing.

(Driving operation)
Next, the compression operation of the compression mechanism (20) in the rotary compressor (1) will be described. Here, the operation of the upper and lower compression sections (20a, 20b) is performed in a state of being shifted from each other by 180 degrees. Since the operations are the same except for the phase, the operation of the upper compression unit (20a) will be described as a representative.

  First, when the electric motor (30) is started, the rotation of the rotor (32) is transmitted to the annular piston (22) of the compression unit (20a) via the drive shaft (33). Then, the piston portion (22a) of the annular piston (22) reciprocates in the radial direction along the blade groove (28) together with the blade (23). Further, the linear portion (22d) of each annular piston (22) reciprocates in the direction perpendicular to the radial direction in the recess (23c) of the blade (23).

  Here, the annular piston (22) slides in the direction perpendicular to the cylinder radial direction with respect to the blade (23) and only moves in the cylinder radial direction together with the blade (23). The displacement in the rotational direction is restricted. That is, the blade (23) constitutes a rotation prevention mechanism that restricts the rotation of the annular piston (22, 22).

  And, by the combination of this radial direction and the reciprocating motion in the direction perpendicular to the radial direction, the piston part (22a) is moved relative to the outer cylinder part (21a) and the inner cylinder part (21b) of each cylinder (21). Revolving, the compression unit (20a) performs a predetermined compression operation.

  Specifically, in the outer cylinder chamber (C1, C3), the volume of the low pressure chamber (C1) is almost the minimum in the state of FIG. 3 (B), from which the drive shaft (33) rotates clockwise in the figure. Then, the volume of the low-pressure chamber (C1) increases with the change to the state of FIG. 3 (C) to FIG. 3 (A), and the refrigerant passes through the suction pipe (14) and the suction port (41). Inhaled into chamber (C1). When the drive shaft (33) makes one revolution and returns to the state of FIG. 3 (B), the suction of the refrigerant into the low pressure chamber (C1) is completed.

  This low-pressure chamber (C1) is now a high-pressure chamber (C3) in which the refrigerant is compressed, and a new low-pressure chamber (C1) is formed across the blade (23). When the drive shaft (33) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (C1), while the volume of the high pressure chamber (C3) decreases, and the refrigerant is compressed in the high pressure chamber (C3). When the pressure in the high pressure chamber (C3) reaches a predetermined value and the differential pressure with respect to the discharge space reaches a set value, the discharge valve is opened by the high pressure refrigerant in the high pressure chamber (C3), and the high pressure refrigerant is discharged from the discharge space to the casing (10 ) Flows out into the high-pressure space (S2).

  On the other hand, in the inner cylinder chambers (C2, C4), the volume of the low-pressure chamber (C2) is almost the minimum in the state of FIG. 3 (F), and the drive shaft (33) rotates clockwise from here. The volume of the low-pressure chamber (C2) increases as the state changes from 3 (G) to FIG. 3 (E), and the refrigerant flows into the suction pipe (14), the suction port (41), and the through hole (44). And is sucked into the low pressure chamber (C2) of the inner cylinder chamber (C2, C4).

  When the drive shaft (33) makes one revolution and again enters the state of FIG. 3 (F), the suction of the refrigerant into the low pressure chamber (C2) is completed. This low-pressure chamber (C2) is now a high-pressure chamber (C4) in which the refrigerant is compressed, and a new low-pressure chamber (C2) is formed across the blade (23). When the drive shaft (33) further rotates, the suction of the refrigerant is repeated in the low pressure chamber (C2), while the volume of the high pressure chamber (C4) decreases, and the refrigerant is compressed in the high pressure chamber (C4). When the pressure in the high pressure chamber (C4) reaches a predetermined value and the differential pressure with respect to the discharge space reaches a set value, the discharge valve is opened by the high pressure refrigerant in the high pressure chamber (C4), and the high pressure refrigerant is discharged from the discharge space to the casing (10 ) Flows out into the high-pressure space (S2).

  In the outer cylinder chambers (C1, C3), refrigerant discharge is started approximately at the timing shown in FIG. 3E, and in the inner cylinder chambers (C2, C4), discharge is started approximately at the timing shown in FIG. The That is, the discharge timings of the outer cylinder chambers (C1, C3) and the inner cylinder chambers (C2, C4) are almost 180 degrees different from each other.

  The sliding part of the compression mechanism (20) is lubricated by the lubricating oil in the storage part (59). Specifically, the lubricating oil in the storage section (59) is compressed by being pushed upward in the oil supply passage (38) of the drive shaft (33) by the oil pump (34) at the lower end of the drive shaft (33). The bearings (16) of the mechanism (20) and the minute gaps between the upper and lower annular pistons (22) are supplied to the inner part of the seal ring (24). Then, the lubricating oil supplied to the inner part flows over the seal ring (24) and flows into the internal space (S1) to increase the pressure in the internal space (S1).

  Here, when the pressure in the internal space (S1) becomes larger than the elastic force of the coil spring of the back pressure adjustment mechanism (35), the fluid inlet of the back pressure adjustment mechanism (35) opens, and the internal space (S1) communicates with the suction port (41), and the pressure in the internal space (S1) decreases. When the pressure in the internal space (S1) becomes smaller than the elastic force of the coil spring of the back pressure adjusting mechanism (35), the fluid inlet of the back pressure adjusting mechanism (35) is closed, and the internal space (S1 ) And the suction port (41) are blocked, and the pressure in the internal space (S1) does not decrease. In this way, by preventing the pressure in the internal space (S1), that is, the back pressure, from rising too much, the annular piston (22, 22) is prevented from being excessively pressed against the cylinder (21, 21). ing.

  The lubricating oil flowing into the internal space (S1) over the seal ring (24) is discharged to the suction port (41) through the back pressure adjusting mechanism (35). The lubricating oil discharged to the suction port (41) is sucked into the compression mechanism (20) together with the refrigerant, compressed in each cylinder chamber (C1, C2, C3, C4), and then into the casing (10). The high pressure space (S2) is discharged to return to the reservoir (59).

  The lubricating oil that has flowed into the internal space (S1) is agitated on the outer peripheral surface of the annular piston (22, 22) by the eccentric rotational movement of each annular piston (22, 22). At this time, even if the annular piston (22, 22) rotates eccentrically, the volume of the internal space (S1) outside the outer peripheral surface of the annular piston (22, 22) is constant. Therefore, the stirring loss of the lubricating oil by the annular piston (22, 22) does not change.

-Effect of the embodiment-
According to this embodiment, unlike the prior art, it is possible to configure the compression mechanism (20) in which the compression parts (20a, 20b) are arranged in two upper and lower stages without using a middle plate. Here, the compression mechanism (20) is configured such that the rotation shafts of the annular pistons (22, 22) are eccentric in opposite directions around the axis of the drive shaft (33).

  As a result, the phases of the volume fluctuation periods in the outer compression chambers (C1, C3) formed in the upper and lower compression sections (20a, 20b) are shifted from each other by 180 degrees, and formed on the upper and lower sides, respectively. The phases of the volume fluctuation periods in the inner compression chambers (C2, C4) are shifted from each other by 180 degrees. From this, the torque fluctuation of the drive shaft (33) generated in the upper compression section (20a) can be offset by the torque fluctuation of the drive shaft (33) generated in the lower compression section (20b), As a whole rotary compressor, the torque fluctuation of the drive shaft (33) can be kept small.

  As described above, it is possible to reduce the cost of the rotary compressor (1) by reducing the middle plate while reducing the vibration and noise due to the torque fluctuation of the drive shaft (33).

  Moreover, according to this embodiment, rotation of each annular piston (22, 22) can be prevented without a middle plate. That is, in the conventional case, since the middle plate is provided between the upper and lower movable members (the cylinder (66) in FIG. 4 and the annular piston in this embodiment), the middle plate is provided between the movable member and the middle plate. It is easy to attach an Oldham joint or the like for preventing the movable member from rotating. However, in the case of this embodiment, since there is no middle plate, it is not easy to attach an Oldham joint or the like. Therefore, according to the present embodiment, the rotation of each annular piston (22, 22) can be prevented by providing the blades (23, 23) with a function of preventing rotation. That is, by arranging the rotation prevention mechanism on the surface side of the piston side end plate (22c, 22c), the back surfaces of the piston side end plate (22c, 22c) can be easily aligned. Thereby, it becomes easy to delete the middle plate provided in the conventional rotary compressor, and the cost of the rotary compressor (1) can be reduced.

  Further, according to the present embodiment, the seal ring (24) can divide a minute gap between the two annular pistons (22, 22) into the inside and the outside of the seal ring (24). Then, by partitioning this minute gap, only the inner part of the seal ring (24) can be brought into a high pressure state. That is, when the diameter of the seal ring (24) is set large, the range of the high pressure state of the minute gap is widened, and the back pressure is increased. On the other hand, when the diameter of the seal ring (24) is set to be small, the back pressure is reduced. Thus, by setting the diameter of the seal ring (24) according to the rotary compressor (1), the annular piston (22, 22) is prevented from being excessively pressed against the cylinder (21, 21). be able to.

  In the conventional case, since the green plate is provided, the annular seal member is provided between the upper surface of the middle plate and the upper movable member, and between the lower surface of the middle plate and the lower movable member. (24) needs to be provided, but in this embodiment, only one seal ring (24) needs to be provided in the minute gap between both annular pistons (22, 22), thereby reducing costs. Can do.

<< Other Embodiments >>
About the said embodiment, it is good also as the following structures.

  In the present embodiment, the annular cylinder chamber (C1, C2, C3, C4) of the cylinder (21) constitutes a compression chamber. However, the present invention is not limited to this, and the annular cylinder chamber (C1, C2, C2) is not limited thereto. C3, C4) may constitute an expansion chamber.

  In this embodiment, in order to make it easy to align the back surfaces of the piston side end plates (22c, 22c), a blade (23 having a rotation prevention mechanism, that is, a recess (23c) on the surface side of the piston side end plates (22c, 22c). However, the present invention is not limited to this. For example, a swing bush that supports the annular pistons (22, 22) in a swingable manner may be provided.

  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 relates to a rotary fluid machine, and in particular, an eccentric rotary piston mechanism including a cylinder having an annular cylinder chamber and an annular piston housed eccentrically in the cylinder chamber in two stages. It is useful for rotating fluid machines arranged one above the other.

It is a longitudinal section of a rotary compressor concerning an embodiment of the present invention. It is a cross-sectional view which shows the compression mechanism of the rotary compressor which concerns on embodiment of this invention. It is a cross-sectional view showing the operation of the compression mechanism. It is a longitudinal cross-sectional view of the conventional rotary compressor.

1 Rotary compressor (rotary fluid machine)
10 Casing 20 Compression mechanism (Eccentric rotation type piston mechanism)
21 cylinder 21a outer cylinder part 21b inner cylinder part 21c cylinder side end plate 22 annular piston 22a piston part 22b bearing part 22c piston side end plate 23 blade 23a outer blade part 23b inner blade part 23c recess 24 seal ring (seal member)
30 Electric motor (drive mechanism)
33 Drive shaft 34 Oil pump (oil supply means)
35 Back pressure adjustment mechanism 36 Communication passage 37 Check valve 38 Oil supply passage (through passage)
41 Suction port 44 Through hole 45 Outer discharge port 46 Inner discharge port

Claims (3)

An eccentric rotary piston mechanism (20) in the casing (10), and a drive mechanism (30) having a drive shaft (33) for driving the eccentric rotary piston mechanism (20);
The eccentric rotary piston mechanism (20) includes a cylinder having an annular cylinder chamber (C1, C2, C3, C4), and an annular cylinder chamber (C1, C2, C3, C4) connected to the outer cylinder chamber (C1, C3) and an inner piston chamber (C2, C4), an annular piston housed eccentrically in the cylinder chamber (C1, C2, C3, C4), an outer cylinder chamber (C1, C3), and an inner cylinder A blade that divides the chamber (C2, C4) into a high-pressure side and a low-pressure side,
The annular piston is a rotary fluid machine that compresses fluid by performing eccentric rotational movement with respect to the cylinder,
The cylinder includes first and second cylinders (21, 21) facing each other in the axial direction, and forms an internal space (S1) between the cylinders (21, 21). It is fixed so that each annular cylinder chamber (C1, C2, C3, C4) is located on both sides in the axial direction.
The annular piston is housed in the internal space (S1) and is composed of first and second annular pistons (22, 22) facing each other in the axial direction, and one end of each of the annular pistons (22, 22) is an end plate ( 22c, 22c), while the rotating shafts of the respective annular pistons (22, 22) are decentered in opposite directions around the axis of the drive shaft (33), the end plates (22c, 22c) Each annular piston (22, 22) is fixed to the drive shaft (33) so that the backs of 22c) are aligned,
An annular seal member (24) is provided so as to be sandwiched between the end plates (22c, 22c) of both the annular pistons (22, 22), and the inside of the seal member (24) is compressed in the casing (10). The high pressure space (S2) where the fluid acts is communicated, the outside of the seal member (24) is communicated with the internal space (S1)
Between the suction port (41) communicating with the cylinder chamber (C1, C2, C3, C4) and the internal space (S1), the fluid pressure of the suction port (41) is higher than the fluid pressure of the suction port (41). ) Is provided with a back pressure adjustment mechanism (35) that holds the internal space (S1) at a pressure lower than the fluid pressure.
Each cylinder (21, 21) is provided with a discharge port (45, 46) for communicating each cylinder chamber (C3, C4) on the high pressure side with the casing (10),
The both annular piston through the through passage (38) passing through the lubricating oil stored in the lower portion of the upper listen pacing (10) from the lower end surface of the drive shaft (33) to the outer peripheral surface of the drive shaft (33) A rotary type characterized in that oil supply means (34) is provided for supplying a sliding surface formed inside the sealing member (24) between the end plates (22c, 22c) of (22, 22). Fluid machinery. In claim 1,
The first and second rotation prevention mechanisms (23, 23) for preventing the rotation of the first and second annular pistons (22, 22) are provided on the end plates (22c, 22c) of the respective annular pistons (22, 22). A rotary fluid machine, wherein the rotary fluid machine is provided on a surface side. In claim 2,
The blade comprises a first blade (23) constituting a first rotation prevention mechanism (23) and a second blade (23) constituting a second rotation prevention mechanism (23),
Each of the annular pistons (22, 22) has a linear part (22d, 22d) continuous with another part in a part of the circumferential direction,
Each of the blades (23, 23) includes an outer blade portion (23a) that partitions the outer cylinder chamber (C1, C3) and an inner blade portion (23b) that partitions the inner cylinder chamber (C2, C4). A recessed portion (slidably fitted to the linear portion (22d) of each annular piston (22, 22) between the outer blade portion (23a) and the inner blade portion (23b). 23c) is formed,
Each cylinder (21, 21) has a blade groove (28) in which the outer blade portion (23a, 23a) and the inner blade portion (23b, 23b) are slidably fitted in the cylinder radial direction. A rotary fluid machine characterized by the above.

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