JP6136519B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor that compresses a fluid by eccentrically rotating a piston with respect to a cylinder.

  Conventionally, a rotary compressor in which a piston rotates eccentrically with respect to a cylinder is known. For example, in the rotary compressor disclosed in Patent Document 1, a plurality of fluid chambers are formed by a pair of pistons and cylinders.

  The rotary compressor disclosed in Patent Document 1 will be described. The piston of the compressor includes an end plate portion, an inner piston portion protruding from the front surface of the end plate portion, and an outer piston portion protruding from the front surface of the end plate portion and surrounding the inner piston portion. Moreover, the inner side recessed part into which an inner side piston part fits in and the outer side recessed part into which an outer side piston part fits are formed in the cylinder of this compressor. In the inner concave portion of the cylinder, the outer side of the inner piston portion is the innermost fluid chamber. In the outer concave portion of the cylinder, the inner side of the outer piston portion serves as an inner fluid chamber, and the outer side of the outer piston portion serves as an outer fluid chamber. In this compressor, the outermost fluid chamber (23d) is formed around the end plate portion of the piston. When the piston rotates eccentrically with respect to the cylinder, a fluid such as a gas refrigerant is sucked into each fluid chamber and compressed.

JP 2011-196270 A

  In the rotary compressor disclosed in Patent Document 1, the front surface of the end plate portion of the piston has a portion between the inner piston portion and the outer piston portion as an intermediate front portion, and a portion outside the outer piston portion is an outer front portion. It becomes. In this piston, the distance from the intermediate front surface portion to the protruding end surface of the outer piston portion is equal to the distance from the outer front surface portion to the protruding end surface of the outer piston. As described above, in the outer concave portion of the cylinder, the inner portion of the outer piston portion serves as the inner fluid chamber, and the outer portion of the outer piston portion serves as the outer front portion. Further, the inner fluid chamber faces the middle front portion, and the outer fluid chamber faces the outer front portion. For this reason, in the rotary compressor of Patent Document 1 in which “the distance from the intermediate front surface portion to the protruding end surface of the outer piston portion” is equal to “the distance from the outer front surface portion to the protruding end surface of the outer piston”, the volume of the inner fluid chamber Is always smaller than the volume of the outer fluid chamber.

  Thus, in the rotary compressor disclosed in Patent Document 1, the volumes of the inner fluid chamber and the outer fluid chamber are different from each other. Then, different amounts of fluid are discharged from each of the inner fluid chamber and the outer fluid chamber at different timings while the piston rotates once. For this reason, in this rotary compressor, the pressure of the fluid discharged from the inner fluid chamber and the outer fluid chamber fluctuates in a complicated manner, and vibration and noise caused by the pressure fluctuation may become a problem.

  This invention is made | formed in view of this point, The objective was discharged from the inner fluid chamber and the outer fluid chamber in the rotary compressor in which a plurality of fluid chambers are formed by a pair of pistons and cylinders. It is to suppress vibration and noise caused by fluid pressure fluctuations.

  A first invention includes a cylinder (21) and a piston (22) that rotates eccentrically with respect to the cylinder (21), and fluid is supplied to a fluid chamber formed by the cylinder (21) and the piston (22). Intended for rotary compressors that inhale and compress. The piston (22) includes a plate-shaped end plate portion (22g), a cylindrical inner piston portion (22a) protruding from the front surface of the end plate portion (22g), and the end plate portion (22g). A cylindrical outer piston portion (22c) projecting from the front surface and surrounding the inner piston portion (22a), and the cylinder (21) has a circular shape into which the inner piston portion (22a) is fitted. An inner recess (21g) in which the outer portion of the inner piston portion (22a) is the innermost fluid chamber (23a) and an annular recess into which the outer piston portion (22c) is fitted, An inner portion of the outer piston portion (22c) serves as an inner fluid chamber (23b), and an outer recess (21k) is formed in which the outer portion of the outer piston portion (22c) serves as an outer fluid chamber (23c). On the other hand, each of the innermost fluid chamber (23a), the inner fluid chamber (23b), and the outer fluid chamber (23c) Is further provided with a blade (24) that partitions the suction side low pressure chamber and the discharge side high pressure chamber, and the piston (22) includes the inner piston portion (22a) and the outer piston of the front surface of the end plate portion (22g). The distance from the intermediate front surface portion (22h), which is a portion between the portions (22c), to the protruding end surface (22d) of the outer piston portion (22c) is the outer piston portion (22g) of the front surface of the end plate portion (22g). 22c) is longer than the distance from the outer front surface portion (22i), which is the outer portion of 22c), to the protruding end surface (22d) of the outer piston portion (22c).

In the first aspect of the invention, in addition to the above-described configuration, the blade (24) is configured so that the innermost fluid chamber (23a) and the inner fluid chamber (23b) are divided into a low pressure chamber on the suction side and a high pressure chamber on the discharge side. A distal end side plate portion (24b) for partitioning, a proximal end side plate portion (24a) for partitioning the outer fluid chamber (23c) into a low pressure chamber on the suction side and a high pressure chamber on the discharge side, the distal end side plate portion (24b) and the proximal end A cylindrical bush portion (24c) disposed between the side plate portions (24a), and the outer piston portion (22c) is partly divided in the circumferential direction, and the end face (C1, C2) ) Is a curved surface that is in sliding contact with the bush portion (24c), and the bush portion (24c) is a cylindrical shape that is formed integrally with the distal end side plate portion (24b) and the proximal end side plate portion (24a). The first part (24h) and the second part formed in a separate cylindrical shape from the first part (24h) and disposed on one end face side of the first part (24h) The end surface of the first portion (24h) on the second portion (24i) side is the outer front surface portion (22i) of the piston (22) in the base end side plate portion (24a). And the same plane as the sliding surface.

  In the first invention, the outer recessed portion (21k) of the cylinder (21) has an inner fluid chamber (23b) at the inner portion of the outer piston portion (22c) and an outer fluid at the outer portion of the outer piston portion (22c). It is a room (23c). The inner fluid chamber (23b) faces the middle front surface (22h) of the end plate (22g) of the piston (22), and the outer fluid chamber (23c) faces the outer front of the end plate (22g) of the piston (22). Facing part (22i). For this reason, suppose that the “distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)” is “from the outer front surface portion (22i) to the protruding end surface (22d) of the outer piston portion (22c)”. The volume of the inner fluid chamber (23b) is necessarily smaller than the volume of the outer fluid chamber (23c).

  On the other hand, the piston (22) according to the first aspect of the invention has a "distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)" 22c) longer than the distance to the tip (22d). Therefore, in the rotary compressor (1) of the present invention, “the distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)” is “the outer piston portion from the outer front surface portion (22i)”. The volume of the inner fluid chamber (23b) becomes larger than when the distance to the protruding end face (22d) of (22c) is equal. That is, in the rotary compressor (1) of the present invention, “the distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)” is “the outer piston portion from the outer front surface portion (22i)”. The volume difference between the inner fluid chamber (23b) and the outer fluid chamber (23c) is reduced compared to the case where the distance to the protruding end surface (22d) of (22c) is equal.

  According to a second invention, in the first invention, the distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c) is determined by the volume of the inner fluid chamber (23b). It is set to be equal to the volume of the outer fluid chamber (23c).

  In the second invention, the volume of the inner fluid chamber (23b) is equal to the volume of the outer fluid chamber (23c). For this reason, the amount of refrigerant discharged from each of the inner fluid chamber (23b) and the outer fluid chamber (23c) matches each time the piston (22) rotates once.

  According to a third invention, in the first or second invention, the piston (22) has a distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a). It is longer than the distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c).

  In the third invention, the inner piston portion (22a) forming the innermost fluid chamber (23a) is surrounded by the outer piston portion (22c) forming the inner fluid chamber (23b) and the outer fluid chamber (23c). It is. For this reason, the “distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a)” is “from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)”. The inner fluid chamber (23a) is necessarily smaller in volume than the inner fluid chamber (23b) and the outer fluid chamber (23c).

  On the other hand, the piston (22) of the third aspect of the invention has a "distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a)" 22c) longer than the distance to the tip (22d). Therefore, in the rotary compressor (1) of the present invention, “the distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a)” is “the intermediate piston portion (22h) to the outer piston portion”. The volume of the innermost fluid chamber (23a) is larger than when the distance to the protruding end surface (22d) of (22c) is equal. In the rotary compressor (1) of the present invention, the set value of the volume of the innermost fluid chamber (23a) is limited by the volume of the inner fluid chamber (23b) and the volume of the outer fluid chamber (23c). No.

  In a fourth aspect based on the third aspect, the cylinder (21) is formed on the cylinder (21) in the radial direction from the side wall surface (21h) of the inner recess (21g) to the outer recess (21k). A guide groove (21r) is formed which extends to the outside of the outer wall surface (21n) and into which the blade (24) is slidably fitted. The cylinder (21) includes the inner recess (21g) and the outer recess (21k). The distance from the intermediate slidable contact surface (21e), which is located between the intermediate slidable contact surface (21e) of the piston (22) and the front surface of the end plate (22g), is the intermediate wall surface (21s). This distance is equal to the distance from the sliding surface (21e) to the bottom wall surface (21i) of the inner recess (21g).

  In the fourth invention, the intermediate sliding surface (21e) of the cylinder (21) is in sliding contact with the intermediate front surface portion (22h) of the end plate portion (22g) of the piston (22). The piston (22) has a “distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a)” “a distance between the intermediate front surface portion (22h) and the protruding end surface of the outer piston portion (22c) (22d). ) Longer than "distance". The inner piston part (22a) fits into the inner recess (21g) of the cylinder (21), and the outer piston part (22c) fits into the outer recess (21k) of the cylinder (21). For this reason, the cylinder (21) has a “distance from the intermediate sliding contact surface (21e) to the bottom wall surface (21i) of the inner recess (21g)” that is “the bottom of the outer recess (21k) from the intermediate sliding contact surface (21e). Longer than the distance to the wall (21p).

  In the fourth invention, the guide groove (21r) is formed in the cylinder (21), and the blade (24) is slidably fitted in the guide groove (21r). The cylinder (21) has a distance from the intermediate sliding contact surface (21e) to the bottom wall surface (21s) of the guide groove (21r) so that the bottom sliding wall surface (21i) of the inner recess (21g) from the intermediate sliding contact surface (21e) Is equal to the distance to For this reason, the blade (24) that divides the innermost fluid chamber (23a) formed in the inner recess (21g) into a low pressure chamber and a high pressure chamber is fitted into the guide groove (21r), so that the intermediate sliding contact surface (21e The inner fluid chamber (23b) and the outer fluid chamber (23c) formed in the outer recess (21k) whose distance from the bottom wall surface is shorter than the inner recess (21g) are also divided into the low pressure chamber and the high pressure chamber.

  In a fifth aspect based on any one of the first to fourth aspects, the cylinder (21) includes an outermost cylinder portion (21c) surrounding the end plate portion (22g) of the piston (22). ), An outermost fluid chamber (23d) is formed between the outer peripheral surface of the end plate portion (22g) of the piston (22) and the inner peripheral surface of the outermost cylinder portion (21c), and the blade (24 ) The innermost fluid chamber (23a), the inner fluid chamber (23b), the outer fluid chamber (23c), and the outermost fluid chamber (23d), respectively, a suction side low pressure chamber and a discharge side high pressure chamber. It divides into two.

  In the fifth invention, the outermost cylinder portion (21c) is provided in the cylinder (21), and the space between the inner peripheral surface of the outermost cylinder portion (21c) and the outer peripheral surface of the end plate portion (22g) of the piston (22). The outermost fluid chamber (23d) is formed at the bottom. Not only the innermost fluid chamber (23a), the inner fluid chamber (23b), and the outer fluid chamber (23c), but also the outermost fluid chamber (23d) is divided into a low pressure chamber and a high pressure chamber by the blade (24).

  In the present invention, the piston (22) of the rotary compressor (1) has a “distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)” as “outer front surface portion (22i). Is longer than the distance “from the protruding end surface (22d) of the outer piston portion (22c)”. Therefore, according to the present invention, “the distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c)” is “the protruding end of the outer piston portion (22c) from the outer front surface portion (22i)”. The volume difference between the inner fluid chamber (23b) and the outer fluid chamber (23c) can be reduced as compared with the case where the distance to the surface (22d) is equal. Therefore, according to the present invention, the difference in the amount of refrigerant discharged from each of the inner fluid chamber (23b) and the outer fluid chamber (23c) during one revolution of the piston (22) can be reduced, and the inner fluid chamber ( 23b) and vibration and noise caused by pressure fluctuations of the fluid discharged from the outer fluid chamber (23c) can be suppressed.

  In the second aspect, the amount of refrigerant discharged from each of the inner fluid chamber (23b) and the outer fluid chamber (23c) can be matched while the piston (22) rotates once. Therefore, according to the present invention, it is possible to further suppress vibration and noise caused by pressure fluctuations of the fluid discharged from the inner fluid chamber (23b) and the outer fluid chamber (23c).

  In the third aspect of the present invention, the piston (22) of the rotary compressor (1) has a "distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a)" It is longer than the distance “(22h) to the protruding end face (22d) of the outer piston part (22c)”. Therefore, the volume of the inner fluid chamber (23b) and the volume of the outer fluid chamber (23c) are adjusted by adjusting the “distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a)”. The volume of the innermost fluid chamber (23a) can be freely set without being restricted by the above. Therefore, according to the present invention, the volume of the innermost fluid chamber (23a) can be set appropriately, and the performance of the rotary compressor (1) can be improved.

  In the fourth aspect of the invention, the guide groove (21r) into which the blade (24) is fitted is formed in the cylinder (21). This cylinder (21) has a distance from the intermediate sliding contact surface (21e) to the bottom wall surface (21s) of the guide groove (21r), and the bottom wall surface (21i) of the inner recess (21g) from the intermediate sliding contact surface (21e). Is equal to the distance to For this reason, the outer recess (21k) whose distance from the intermediate sliding contact surface (21e) to the bottom wall surface is shorter than the inner recess (21g) by the blade (24) that partitions the innermost fluid chamber (23a) into the low pressure chamber and the high pressure chamber. The inner fluid chamber (23b) and the outer fluid chamber (23c) formed in () can also be divided into a low pressure chamber and a high pressure chamber.

  The rotary compressor (1) according to the fifth aspect of the invention has an outermost fluid chamber (23d) in addition to the innermost fluid chamber (23a), the inner fluid chamber (23b), and the outer fluid chamber (23c). It is formed. That is, in the present invention, four fluid chambers (23a to 23d) are formed by a pair of cylinder (21) and piston (22). For this reason, if a refrigerant | coolant is sequentially compressed in each fluid chamber (23a-23d), for example, a four-stage compressor can be comprised by a set of cylinder (21) and piston (22). Therefore, according to this invention, the use of the rotary compressor (1) is expanded by increasing the number of fluid chambers (23a to 23d) formed by a pair of cylinders (21) and pistons (22). be able to.

FIG. 1 is a longitudinal sectional view of a rotary compressor of Reference Technique 1 . FIG. 2 is an enlarged cross-sectional view of the compression mechanism of FIG. Figure 3 is a longitudinal sectional view showing a different cross-section and Figure 2 of the compression mechanism reference technology 1. 4A and 4B are cross-sectional views of the compression mechanism of Reference Technique 1 , wherein FIG. 4A shows the AA cross section and the CC cross section of FIG. 2, and FIG. 4B shows the BB cross section and D of FIG. -D shows a cross section. 5 (A) is a longitudinal sectional view showing the same cross section as FIG. 2 of the first cylinder and the second cylinder, and FIG. 5 (B) is a longitudinal sectional view showing the same cross section as FIG. 2 of the first piston and the second piston. FIG. 6 is a cross-sectional view of the first cylinder and the second cylinder in the EE cross section and the FF cross section in FIG. 3. FIG. 7 is a longitudinal sectional view of the first cylinder and the second cylinder showing the JJ section of FIG. 6. FIG. 8 is a cross-sectional view of the first piston and the second piston in the GG section and the HH section in FIG. 3. FIG. 9 is a longitudinal sectional view of the first piston and the second piston showing the KK cross section of FIG. 8. FIG. 10 is a perspective view of the first blade and the second blade of Reference Technique 1. FIG. FIG. 11 is a transverse cross-sectional view of the compression mechanism portion showing the same cross section as FIG. 4A, and shows the state of the compression mechanism portion where the rotation angle of the drive shaft is every 90 °. FIG. 12 is a transverse cross-sectional view of the compression mechanism portion showing the same cross section as FIG. 4B, and shows the state of the compression mechanism portion where the rotation angle of the drive shaft is every 90 °. FIG. 13 is a perspective view of the first blade and the second blade of the first embodiment. FIG. 14 is a longitudinal sectional view of a rotary compressor showing the compression mechanism of Reference Technique 2 in an enlarged manner. 15 is a longitudinal sectional view showing a cross section different from that of FIG. 14 of the compression mechanism of Reference Technique 2. FIG. 16A is a longitudinal sectional view showing the same cross section as FIG. 14 of the first cylinder and the second cylinder, and FIG. 16B is a longitudinal sectional view showing the same cross section as FIG. 14 of the first piston and the second piston. FIG. 17 is a cross-sectional view of the first cylinder and the second cylinder in the EE cross section and the FF cross section in FIG. 15. FIG. 18 is a longitudinal sectional view of the first cylinder and the second cylinder showing the JJ section of FIG. 17. FIG. 19 is a perspective view of the first blade and the second blade of Reference Technique 2 . FIG. 20 is a perspective view of the first blade and the second blade of the second embodiment. FIG. 21 is a longitudinal sectional view of a rotary compressor showing the compression mechanism of the third embodiment in an enlarged manner.

  Embodiments of the present invention will be described in detail with reference to the drawings. Note that the embodiments and modifications described below are essentially preferable examples, and are not intended to limit the scope of the present invention, its application, or its use.

<< Reference Technology 1 >>
Reference technique 1 will be described. The compressor (1) of the present reference technology is provided in a refrigerant circuit that performs a refrigeration cycle, and compresses the refrigerant.

-Overall configuration of compressor-
As shown in FIG. 1, the compressor (1) of this reference technology is a hermetic rotary compressor. The casing (10) of the compressor (1) houses a compression mechanism (40) and an electric motor (50) for driving the compression mechanism (40). In the casing (10), the compression mechanism (40) is disposed below the electric motor (50).

  The casing (10) is formed in an upright cylindrical shape. Specifically, the casing (10) includes a cylindrical body (11), an upper end panel (12) that closes the upper end of the body (11), and a lower end panel (that closes the lower end of the body (11) ( 13). The body (11) includes a suction pipe (61, 62, 63, 64) for introducing the refrigerant into the compression mechanism (40) and a discharge pipe for extracting the refrigerant compressed in the compression mechanism (40). (66, 67, 68, 69) are provided through. The upper end plate (12) is also provided with a d fourth discharge pipe (69) through which the refrigerant compressed in the compression mechanism (40) is led out.

  The electric motor (50) includes a stator (51) and a rotor (52). The stator (51) is fixed to the body (11) of the casing (10). The rotor (52) is disposed inside the stator (51). The rotor (52) is attached to the drive shaft (53) of the compression mechanism (40).

-Configuration of compression mechanism-
As shown in FIG. 2, the compression mechanism (40) includes two cylinders (21, 31) and pistons (22, 32), a front head (16), a middle plate (25), and a rear head (19). And a drive shaft (53). The compression mechanism (40) is fixed to the body (11) of the casing (10).

  In the compression mechanism (40), the rear head (19), the second cylinder (31), the middle plate (25), the first cylinder (21), and the front head (16) in order from bottom to top. Are stacked. The first piston (22) is accommodated in a space surrounded by the first cylinder (21) and the middle plate (25). The second piston (32) is accommodated in a space surrounded by the second cylinder (31) and the middle plate (25). The drive shaft (53) is provided so as to penetrate the compression mechanism (40) vertically.

<Drive shaft>
The drive shaft (53) has a first eccentric portion (53a) and a second eccentric portion (53b) formed in the lower portion thereof. Further, as described above, the rotor (52) of the electric motor (50) is attached to the upper portion of the drive shaft (53).

  The first eccentric portion (53a) is formed in a cylindrical shape having a larger diameter than the main shaft portion above the first eccentric portion (53a), and is eccentric from the axis of the drive shaft (53) by a predetermined distance.

  The second eccentric portion (53b) is formed in a cylindrical shape having the same diameter as the first eccentric portion (53a), and is eccentric from the axis of the drive shaft (53) by the same distance as the first eccentric portion (53a). That is, the amount of eccentricity of the second eccentric portion (53b) (that is, the distance from the axis of the drive shaft (53) to the axis of the second eccentric portion (53b)) is the amount of eccentricity of the first eccentric portion (53a). (That is, equal to the distance from the axis of the drive shaft (53) to the axis of the first eccentric portion (53a)).

  The second eccentric portion (53b) is eccentric to the opposite side of the first eccentric portion (53a) with respect to the axis of the drive shaft (53). That is, the first eccentric part (53a) and the second eccentric part (53b) are arranged so that their phases are shifted by 180 ° with the axis of the drive shaft (53) as the center. As will be described later, the first eccentric portion (53a) engages with the first piston (22), and the second eccentric portion (53b) engages with the second piston (32).

  Although not shown, an oil supply passage is formed in the drive shaft (53). The lubricating oil collected at the bottom of the casing (10) is supplied to the compression mechanism (40) through the oil supply passage of the drive shaft (53).

<Front head>
The front head (16) is disposed on the first cylinder (21). The front head (16) includes a disk-shaped flat plate portion (16a) and a bearing portion (16b) formed integrally with the flat plate portion (16a). 2, in the front head (16), the lower surface of the flat plate portion (16a) is in contact with the upper surface of the first cylinder (21).

  A through hole (16c) for inserting the drive shaft (53) is formed in the central portion of the flat plate portion (16a). The bearing portion (16b) is formed in a cylindrical shape extending upward from the peripheral edge portion of the through hole (16c) of the flat plate portion (16a). A cylindrical bearing metal (16d) for rotatably supporting the drive shaft (53) is fitted into the bearing portion (16b).

  A muffler member (27) is attached to the front head (16). The muffler member (27) is provided so as to cover the upper surface of the flat plate portion (16a) in FIG. 2, and forms a muffler space (27a) between the upper surface of the flat plate portion (16a). A gap is formed between the outer peripheral surface of the bearing portion (16b) and the muffler member (27) for extracting the refrigerant from the muffler space (27a).

<First piston and first cylinder>
The first piston (22) and the first cylinder (21) form a first compression mechanism (20) together with a first blade (24) described later. As will be described in detail later, in the first compression mechanism section (20), the innermost fluid chamber (23a), the inner fluid chamber (23b), and the outer fluid chamber (by the first piston (22) and the first cylinder (21)). 23c) and the outermost fluid chamber (23d) are formed.

  As shown in FIGS. 4 (A) and 5 (B), the first piston (22) includes an end plate portion (22g), an inner piston portion (22a), and an outer piston portion (22c). The end plate part (22g) is formed in a slightly thick disk shape. The inner piston portion (22a) and the outer piston portion (22c) are cylindrical portions protruding from the front surface of the end plate portion (22g), and are formed integrally with the end plate portion (22g).

  The inner diameter of the outer piston part (22c) is larger than the outer diameter of the inner piston part (22a). That is, the outer piston part (22c) is disposed so as to surround the inner piston part (22a). Further, the axis of the inner piston part (22a) coincides with the axis of the outer piston part (22c). That is, the inner piston part (22a) and the outer piston part (22c) are arranged coaxially. Further, the outer piston portion (22c) is a cut-down portion (22f) in which a portion facing a later-described suction port (P2) is one step lower than the other portions.

  The first piston (22) has a through hole (22e) extending from the protruding end surface (22b) of the inner piston portion (22a) to the back surface (22k) of the end plate portion (22g). The through hole (22e) is a hole having a circular cross section coaxial with the inner piston portion (22a). The first eccentric portion (53a) of the drive shaft (53) is inserted through the through hole (22e). The first piston (22) is driven by a first eccentric part (53a) inserted through the through hole (22e).

The front face of the end plate part (22g) of the first piston (22) is the intermediate front face part (22h) between the inner piston part (22a) and the outer piston part (22c), and the outer side of the outer piston part (22c). This is the outer front part (22i). As shown in FIG. 5B, the first piston (22) has a distance H ₁ (that is, the inner piston portion (22a) from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a). )) Is equal to the distance H ₂ from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c) (that is, the height of the outer piston portion (22c)). The first piston (22), from the middle front portion (22h) the outer piston section is a distance of H ₂ up to the protruding end surfaces (22 d) of (22c), an outer front portion from (22i) the outer piston portion (22c) longer than the distance H ₃ to the protruding end surfaces (22 d).

As shown in FIGS. 4A, 8, and 9, the inner piston portion (22a) has a notch (n1) formed on the outer peripheral portion thereof. The notch (n1) forms a curved surface that can always slide in contact with the tip side plate (24b) of the first blade (24) described later. The outer piston portion (22c) is partially cut in the circumferential direction. The end faces (C1, C2) of the part where the outer piston part (22c) is divided are curved surfaces that are in sliding contact with the bush part (24c) of the first blade (24) described later.

  Further, the end portion (22g) has a notch (n2) formed on the outer periphery thereof. The notch (n2) forms a curved surface that is always slidable in contact with the short part (24e) of the first blade (24) described later.

As shown in FIG. 8, the outer piston portion (22c) is divided at one place in the circumferential direction. The end face (C1, C2) of the part where the outer piston part (22c) is divided is a circular arc surface having a common curvature center, and is in sliding contact with a bush part (24c) of the first blade (24) described later (FIG. 4 ( See A)).

  As shown in FIGS. 4A and 5A, the first cylinder (21) is a member formed in a substantially circular thick plate shape. The first cylinder (21) is formed with a cylinder side sliding contact surface (21d), an inner recess (21g), and an outer recess (21k). The cylinder side sliding contact surface (21d) is a flat surface that is in sliding contact with the front surface of the end plate portion (22g) of the first piston (22). The inner recess (21g) is a circular recess that opens in the cylinder-side sliding contact surface (21d), and is formed at the center of the first cylinder (21). The outer recess (21k) is an annular recess that opens to the cylinder side sliding contact surface (21d) and is formed so as to surround the inner recess (21g). That is, the radius of curvature of the inner wall surface (21m) of the outer recess (21k) is larger than the radius of curvature of the side wall surface (21h) of the inner recess (21g).

As shown in FIG. 5 (A), the cylinder side sliding contact surface (21d) of the first cylinder (21) has an intermediate sliding contact surface (21e) between the inner recess (21g) and the outer recess (21k). Thus, the outer portion of the outer recess (21k) becomes the outer sliding contact surface (21f). The first cylinder (21) has a distance L ₁ from the intermediate sliding contact surface (21e) to the bottom wall surface (21i) of the inner recess (21g) (that is, the depth of the inner recess (21g)). It is equal to the distance L ₂ (that is, the depth of the outer recess (21k)) from (21e) to the bottom wall surface (21p) of the outer recess (21k). The first cylinder (21), the intermediate sliding surface (21e) distance L ₂ to the bottom wall surface of the outer recess (21k) (21p) is from the outer sliding surface (21f) of the outer recess (21k) longer than the distance L ₃ to the bottom wall (21p).

  In the first cylinder (21), the portion between the inner recess (21g) and the outer recess (21k) becomes the inner cylinder portion (21a), and the portion outside the outer recess (21k) is the outer cylinder portion (21b). Become. In FIG. 5A, the lower surface of the inner cylinder portion (21a) is the intermediate sliding contact surface (21e), and the lower surface of the outer cylinder portion (21b) is the outer sliding contact surface (21f).

  Moreover, the outermost cylinder part (21c) is formed in the 1st cylinder (21). The outermost cylinder portion (21c) is an annular portion formed so as to surround the cylinder side sliding contact surface (21d). In FIG. 5A, the outermost cylinder part (21c) protrudes below the cylinder side sliding contact surface (21d). The projecting end surface of the outermost cylinder portion (21c) is in close contact with the middle plate (25).

As shown in FIG. 2, the inner piston part (22a) of the first piston (22) is fitted into the inner recess (21g) of the first cylinder (21). The depth L ₁ of the inner recess (21g) has a height H ₁ is substantially equal to the inner piston portion (22a). Therefore, the protruding end surface (22b) of the inner piston portion (22a) is in sliding contact with the bottom wall surface (21i) of the inner recess (21g), and the intermediate front surface portion (22h) of the first piston (22) is the first cylinder ( 21) is in sliding contact with the intermediate sliding contact surface (21e). Moreover, as shown in FIG. 4, the outer peripheral surface of the inner piston portion (22a) is in sliding contact with the side wall surface (21h) of the inner recess (21g) at one place in the circumferential direction.

  The inner concave portion (21g) of the first cylinder (21) has an outer portion of the inner piston portion (22a) (that is, an outer peripheral surface of the inner piston portion (22a) and a side wall surface (21h) of the inner concave portion (21g). The portion sandwiched between the two is the innermost fluid chamber (23a).

As shown in FIG. 2, the outer piston part (22c) of the first piston (22) is fitted into the outer recess (21k) of the first cylinder (21). The depth L ₂ of the outer recess (21k) is the outer piston portion (32c) the height H ₂ and substantially equal. The distance from the outer sliding surface (21f) a distance L ₃ of the bottom to the wall surface (21p) of the outer recess (21k), an outer front portion from (22i) to the protruding end surface of the outer piston portion (22c) (22d) H ₃ substantially equal. Accordingly, the protruding end surface (22d) of the outer piston portion (22c) is in sliding contact with the bottom wall surface (21p) of the outer recess (21k), and the outer front surface portion (22i) of the first piston (22) is 21) It is in sliding contact with the outer sliding contact surface (21f). As shown in FIG. 4, the inner peripheral surface of the outer piston portion (22c) is in sliding contact with the inner wall surface (21m) of the outer concave portion (21k) at one place in the circumferential direction, and the outer piston portion (22c) The outer peripheral surface is in sliding contact with the outer wall surface (21n) of the outer recess (21k) at one place in the circumferential direction.

  The outer concave portion (21k) of the first cylinder (21) is an inner portion of the outer piston portion (22c) (that is, the inner peripheral surface of the outer piston portion (22c) and the inner wall surface (21m) of the outer concave portion (21k). ) Is the inner fluid chamber (23b), the outer part of the outer piston part (22c) (that is, the outer peripheral surface of the outer piston part (22c) and the outer wall surface (21n) of the outer recess (21k)) The portion sandwiched between the outer fluid chambers becomes the outer fluid chamber (23c).

As described above, the first piston (22), the distance of H ₂ up to the protruding end surfaces (22 d) of the outer piston portion from the middle front portion (22h) (22c) is the outer piston portion from the outer front face (22i) ( longer than the distance H ₃ to the protruding end surfaces of 22c) (22d). Distance of H ₂ up to the protruding end surfaces (22 d) of the outer piston portion from the middle front portion (22h) (22c) is a value such that the volume of the inner fluid chamber (23b) is equal to the volume of the outer fluid chamber (23c) Is set. Therefore, in the first compression mechanism section (20), when the rotation angle of the drive shaft (53) shown in FIG. 11A is 0 ° (that is, the first blade (24) is the first cylinder (21)). The volume of the outer fluid chamber (23c) when it is positioned at the outermost position is such that the rotation angle of the drive shaft (53) shown in FIG. 11C is 180 ° (that is, the first blade (24) is the first. It becomes substantially equal to the volume of the inner fluid chamber (23b) of the cylinder (21) located closest to the center.

The end plate part (22g) of the first piston (22) is surrounded by the outermost cylinder part (21c) of the first cylinder (21). Distance L ₄ to the protruding end surfaces of the outermost cylinder portion from the outer sliding surface (21f) (21c) is substantially equal to the thickness H ₄ of the outer peripheral portion of the end plate portion of the first piston (22) (22g) (See FIG. 5). The space sandwiched between the outer peripheral surface of the end plate portion (22g) of the first piston (22) and the inner peripheral surface of the outermost cylinder portion (21c) of the first cylinder (21) is the outermost fluid chamber (23d). It becomes.

  A through hole (21q) is formed in the center of the first cylinder (21). The through hole (21q) is a circular hole that opens in the bottom wall surface (21i) of the inner recess (21g). The through hole (21q) is a hole for inserting the drive shaft (53).

As shown in FIGS. 6 and 7, the first cylinder (21) is formed with a guide groove (21r) into which the first blade (24) is slidably fitted. The guide groove (21r) is a straight concave groove extending in the radial direction of the first cylinder (21). The guide groove (21r) is formed from the inner cylinder part (21a) to the outer cylinder part (21b) and the outermost cylinder part (21c).
That is, the guide groove (21r) extends from the side wall surface (21h) of the inner recess (21g) to the outer side of the outer wall surface (21n) of the outer recess (21k). The bottom wall surface (21s) of the guide groove (21r), the bottom wall surface (21i) of the inner recess (21g), and the bottom wall surface (21p) of the outer recess (21k) form the same plane.

<First blade>
As shown in FIG. 10, the first blade (24) is a member in which a base end side plate portion (24a), a tip end side plate portion (24b), and a bush portion (24c) are integrally formed. Moreover, the base end side board part (24a) is comprised by the elongate part (24d) and the short part (24e).

The proximal end side plate portion (24a) is a thick plate portion. Moreover, as for the base end side board part (24a), each of the elongate part (24d) and the short part (24e) is formed in the rectangular-plate shape. Elongated section (24d), the length of the short side at V1 length of the long side has a rectangular plate-shaped portion of the W _1. The length W ₁ of the short sides of the elongated portion (24d) is substantially the distance H ₃ to the protruding end surfaces (22 d) of the outer piston portion from the outer front face (22i) of the first piston (22) (22c) be equivalent to. Short portion (24e), the length of the short side at V2 length of the long side has a rectangular plate-shaped portion of the W _2. The length W ₂ of the short side of the short portion (24e) is substantially equal to the thickness H ₄ of the outer peripheral portion of the end plate portion of the first piston (22) (22g).

  In the base end side plate portion (24a), the short portion (24e) is continuously formed on one of the side surfaces (the lower surface in FIG. 10) along the long side of the long portion (24d). The base end surface (one of the side surfaces along the short side) of the long portion (24d) and the base end surface (one of the side surfaces along the short side) of the short portion (24e) form the same plane. Yes. Moreover, as for the short length part (24e), the front end surface (24g) which is the other of the side surfaces along the short side becomes a circular arc surface.

Bush (24c) is a portion where the diameter length at d is formed in a cylindrical shape of W _3. The bush portion (24c) is formed continuously at the distal end of the elongated portion (24d) of the proximal end side plate portion (24a). The central axis of the bush portion (24c) is substantially parallel to the short side of the long portion (24d). In FIG. 10, the upper end surface of the bush portion (24c) forms the same plane as the upper surface of the long portion (24d).

The diameter d of the bush portion (24c) is substantially equal to twice the radius of curvature r of the end face (C1, C2) of the split portion of the outer piston portion (22c ) in the first piston (22) (d = 2r). . The height W ₃ of the bushing portion (24c), the distance H ₂ and substantially equal to the middle front portion of the first piston (22) from (22h) to the protruding end surface of the outer piston portion (22c) (22 d).

The distal end side plate portion (24b) is a rectangular plate portion, and is disposed on the opposite side of the proximal end side plate portion (24a) with the bush portion (24c) interposed therebetween. Distal side plate portion (24b), the length W ₄ bush portion of the short side (24c) of height W ₃ substantially equal, the short side a central axis substantially parallel bushes (24c) is there. That is, the length W ₄ of the short side of the front end plate portion (24b) includes a distance of H ₂ middle front portion of the first piston (22) from (22h) to the protruding end surface of the outer piston portion (22c) (22 d) substantially equal, the distance H ₁ is substantially equal to the middle front portion of the first piston (22) from (22h) to the protruding end surfaces of the inner piston portion (22a) (22b).

  In FIG. 10, the upper side surface of the tip side plate portion (24b) forms the same plane as the upper end surface of the bush portion (24c), and the lower side surface of the tip side plate portion (24b) is the lower end surface of the bush portion (24c). And form the same plane. Moreover, as for the front end side plate part (24b), the front end surface (24f) located on the opposite side to the bush part (24c) is an arc surface.

As shown in FIGS. 3 and 4, the first blade (24) has a bush portion (24c) fitted into a part of the outer piston portion (22c) of the first piston (22), and the bush portion (24c ) Is in sliding contact with the end face (C1, C2) of the split part of the outer piston part (22c) . The first blade (24) is slidably fitted into the guide groove (21r) of the first cylinder (21), and is in sliding contact with the side wall of the guide groove (21r).

  The distal end side plate portion (24b) is in sliding contact with the side wall of the portion of the guide groove (21r) formed in the inner cylinder portion (21a). The tip side plate (24b) partitions the innermost fluid chamber (23a) and the inner fluid chamber (23b) into a high pressure chamber (23aH, 23bH) and a low pressure chamber (23aL, 23bL). Further, the long portion (24d) of the base end side plate portion (24a) is in sliding contact with the side wall of the portion of the guide groove (21r) formed in the outer cylinder portion (21b). The elongated portion (24d) partitions the outer fluid chamber (23c) into a high pressure chamber (23cH) and a low pressure chamber (23cL). Further, the short portion (24e) of the base end side plate portion (24a) is in sliding contact with the side wall of the portion of the guide groove (21r) formed in the outermost cylinder portion (21c). The short part (24e) partitions the outermost fluid chamber (23d) into a high pressure chamber (23dH) and a low pressure chamber (23dL).

  As described above, the first blade (24) is configured so that each of the four fluid chambers (23a, 23b, 23c, 23d) formed in the first compression mechanism section (20) is replaced with the high-pressure chamber (23aH, 23bH, 23cH, 23dH) and low pressure chamber (23aL, 23bL, 23cL, 23dL). That is, the first blade (24) partitions the four fluid chambers (23a, 23b, 23c, 23d) of the first compression mechanism section (20) in the respective circumferential directions. Each of the innermost fluid chamber (23a), the inner fluid chamber (23b), the outer fluid chamber (23c), and the outermost fluid chamber (23d) is a low-pressure chamber (the right portion of the first blade (24) in FIG. 4). 23aL, 23bL, 23cL, 23dL), and the left part of the first blade (24) in FIG. 4 is a high-pressure chamber (23aH, 23bH, 23cH, 23dH).

<Second piston and second cylinder>
The second piston (32) and the second cylinder (31) form a second compression mechanism (30) together with a second blade (34) described later. As will be described in detail later, in the second compression mechanism (30), the innermost fluid chamber (33a), the inner fluid chamber (33b), and the outer fluid chamber (33c) are separated by the second piston (32) and the second cylinder (31). ), And the outermost fluid chamber (33d).

  As shown in FIGS. 4A and 5B, the second piston (32) is a member having the same shape as the first piston (22). However, the second piston (32) is provided in the compression mechanism (40) in an upside-down posture with respect to the first piston (22).

The second piston (32) includes an end plate portion (32g) and an inner piston portion (32a) and an outer piston portion (32c) protruding from the front surface of the end plate portion (32g). A cut-down portion (32f) is formed in the outer piston portion (32c). The front surface of the end plate part (32g) of the second piston (32) is the middle front part (32h) between the inner piston part (32a) and the outer piston part (32c), and the outer side of the outer piston part (32c). Is the outer front surface (32i). Further, a notch (n1) is formed in the inner piston part (32a), and a notch (n2) is formed in the end plate part (22g) (see FIG. 4). Further, the end faces (C1, C2 ) of the dividing portion of the outer piston part (32c) are circular arc surfaces having a common center of curvature, and are in sliding contact with the bush part (34c) of the second blade (34) described later (FIG. 4 (A)).

  The second piston (32) is formed with a through hole (32e) through which the second eccentric portion (53b) of the drive shaft (53) is inserted. The second piston (32) is driven by the second eccentric part (53b) inserted through the through hole (32e).

  As shown in FIGS. 4A and 5A, the second cylinder (31) is a member having the same shape as the first cylinder (21). However, the second cylinder (31) is provided in the compression mechanism (40) in an upside down orientation with respect to the first cylinder (21).

  The second cylinder (31) has a cylinder side sliding contact surface (31d), an inner recess (31g), and an outer recess (31k). The cylinder side slidable contact surface (31d) of the second cylinder (31) has an intermediate slidable contact surface (31e) between the inner recess (31g) and the outer recess (31k). The portion becomes the outer sliding contact surface (31f). Further, in the second cylinder (31), the portion between the inner recess (31g) and the outer recess (31k) becomes the inner cylinder portion (31a), and the portion outside the outer recess (31k) is the outer cylinder portion (31b). )

  An outermost cylinder portion (31c) is formed in the second cylinder (31). The projecting end surface of the outermost cylinder portion (31c) is in close contact with the middle plate (25). A through hole (31q) for inserting the drive shaft (53) is formed at the center of the second cylinder (31). As shown in FIGS. 6 and 7, the second cylinder (31) is formed with a guide groove (31r) into which the second blade (34) is slidably fitted. The guide groove (31r) is formed from the inner cylinder part (31a) to the outer cylinder part (31b) and the outermost cylinder part (31c).

  As shown in FIG. 2, the inner piston portion (32a) of the second piston (32) is fitted into the inner recess (31g) of the second cylinder (31), and the outer recess (31k) of the second cylinder (31) is fitted. ) Fits the outer piston portion (32c) of the second piston (32). The protruding end surface (32b) of the inner piston portion (32a) is in sliding contact with the bottom wall surface (31i) of the inner recessed portion (31g), and the protruding end surface (32d) of the outer piston portion (32c) is the bottom of the outer recessed portion (31k). Touch the wall (31p). The intermediate front surface portion (32h) is in sliding contact with the intermediate sliding contact surface (31e), and the outer front surface portion (32i) is in sliding contact with the outer sliding contact surface (31f).

  As shown in FIG. 4, the inner recess (31g) of the second cylinder (31) has an outer portion of the inner piston portion (32a) (that is, the outer peripheral surface of the inner piston portion (32a) and the inner recess (31g). The portion sandwiched between the side wall surfaces (31h) becomes the innermost fluid chamber (33a). In addition, the outer recess (31k) of the second cylinder (31) has an inner portion of the outer piston portion (32c) (that is, the inner wall surface (31m) of the outer recess (31k) and the inner periphery of the outer piston portion (32c)). The portion sandwiched between the surfaces becomes the inner fluid chamber (33b), and the outer portion of the outer piston portion (32c) (that is, the outer wall surface (31n) of the outer recess (31k) and the outer peripheral surface of the outer piston portion (32c)) The portion sandwiched between the outer fluid chambers is the outer fluid chamber (33c).

Similar to the first piston (22), the second piston (32), the distance of H ₂ up to the protruding end surfaces (32d) of the outer piston portion from the middle front portion (32h) (32c) is an outer front face (3i) from longer than the distance H ₃ to the protruding end surface of the outer piston portion (32c) (32d). In the second compression mechanism section (30), the outer fluid chamber (in the state shown in FIG. 11A) when the second blade (34) is positioned on the outermost side of the second cylinder (31). 33c) is the volume of the inner fluid chamber (33b) when the second blade (34) is located closest to the center of the second cylinder (31) (that is, in the state shown in FIG. 11C). Substantially equal.

  The end plate part (32g) of the second piston (32) is surrounded by the outermost cylinder part (31c) of the second cylinder (31). The space sandwiched between the outer peripheral surface of the end plate portion (32g) of the second piston (32) and the inner peripheral surface of the outermost cylinder portion (31c) of the second cylinder (31) is the outermost fluid chamber (33d). .

<Second blade>
As shown in FIG. 10, the second blade (34) is a member having the same shape as the first blade (24). The second blade (34) includes a long portion (34a), a short portion (34b), and a bush portion (34c).

As shown in FIGS. 3 and 4, the second blade (34) is slidably fitted in the guide groove (31r) of the second cylinder (31). In addition, the second blade (34) has a long end portion (34a) having a distal end surface (34f) that is in sliding contact with a notch portion (n1) of the inner piston portion (32a) of the second piston (32). ) Is in sliding contact with the notch (n2) of the end plate (32g) of the second piston (32). Further, in the second blade (34), the outer peripheral surface of the bush portion (34c) is in sliding contact with the end surface (C1, C2) of the divided portion of the outer piston portion ( 32c ) of the second piston (32).

  As shown in FIG. 4, the second blade (34) includes four fluid chambers (33a, 33b, 33c, 33d) formed in the second compression mechanism (30), and the high pressure chambers (33aH, 33bH). , 33cH, 33dH) and a low pressure chamber (33aL, 33bL, 33cL, 33dL). That is, the second blade (34) partitions the four fluid chambers (33a, 33b, 33c, 33d) of the second compression mechanism (30) in the respective circumferential directions. Each of the innermost fluid chamber (33a), the inner fluid chamber (33b), the outer fluid chamber (33c), and the outermost fluid chamber (33d) has a low pressure chamber (the right side portion of the second blade (34) in FIG. 33aL, 33bL, 33cL, 33dL), and the left part of the second blade (34) in FIG. 4 is a high-pressure chamber (33aH, 33bH, 33cH, 33dH).

<Middle plate>
As shown in FIG. 2, the middle plate (25) includes a main body (25a) and a lid (25b) stacked in the axial direction of the drive shaft (53). In the middle plate (25), the lid (25b) is disposed below the main body (25a). The main body (25a) is formed in a thick disk shape. The lid part (25b) is formed in a disk shape that is thinner than the main body part (25a).

  A through hole (25c) that extends over both the main body (25a) and the lid (25b) is formed at the center of the middle plate (25). The drive shaft (53) is inserted through the through hole (25c).

  In FIG. 2, the upper surface of the main body (25a) is in close contact with the protruding end surface (lower surface) of the outermost cylinder (21c) of the first cylinder (21), and the lower surface is in close contact with the upper surface of the lid (25b). To do. The upper surface of the main body (25a) faces the outermost fluid chamber (23d) of the first compression mechanism (20). The upper surface of the main body (25a) is in sliding contact with the rear surface (22k) of the end plate portion (22g) of the first piston (22). The main body (25a) constitutes the first compression mechanism (20) together with the first piston (22) and the first cylinder (21).

  In FIG. 2, the lower surface of the lid portion (25b) is in close contact with the protruding end surface (upper surface) of the outermost cylinder portion (31c) of the second cylinder (31). The lower surface of the lid part (25b) faces the outermost fluid chamber (33d) of the second compression mechanism part (30). Further, the lower surface of the lid portion (25b) is in sliding contact with the back surface (32k) of the end plate portion (32g) of the second piston (32). The lid (25b) constitutes the second compression mechanism (30) together with the second piston (32) and the second cylinder (31).

<Rear head>
The rear head (19) is disposed below the second cylinder (31). The rear head (19) includes a disk-shaped flat plate portion (19a) that is superimposed on the lower surface of the second cylinder (31), and a bearing portion (19b) that is formed integrally with the flat plate portion (19a). In FIG. 2, in the rear head (19), the upper surface of the flat plate portion (19a) is in contact with the lower surface of the second cylinder (31).

  A through hole (19c) through which the drive shaft (53) is inserted is formed at the center of the flat plate portion (19a). The bearing portion (19b) is formed in a cylindrical shape extending upward from the peripheral edge portion of the through hole (19c) of the flat plate portion (19a). A cylindrical bearing metal (19d) for rotatably supporting the drive shaft (53) is fitted into the inner peripheral surface of the bearing portion (19b).

<Hydraulic introduction path>
As shown in FIG. 3, a hydraulic pressure introduction path (110) is formed in the compression mechanism (40). The hydraulic pressure introduction path (110) is formed in the middle plate (25) and the rear head (19). The part formed in the middle plate (25) of the oil introduction path (110) is connected to the outer end of the guide groove (21r) of the first cylinder (21) and the guide groove (31r of the second cylinder (31)). ). A portion of the oil introduction path (110) formed in the rear head (19) is formed by an oil introduction pipe extending downward from the rear head (19) at the outer end of the guide groove (31r) of the second cylinder (31). 111) In each compression mechanism section (20, 30), the pressure of the lubricating oil accumulated at the bottom of the casing (10) acts on the base end face of the blade (24, 34).

<Suction port, discharge port>
Each of the first compression mechanism section (20) and the second compression mechanism section (30) has three suction ports (P1, P2, P3) and four discharge ports (P11, P12, P13, P14). Is formed.

  As shown in FIG. 2, the first suction port (P1) and the first discharge port (P11) are formed in the middle plate (25). The first suction port (P1) and the first discharge port (P11) of the first compression mechanism section (20) are opened on the upper surface of the main body (25a) of the middle plate (25). The first suction port (P1) and the first discharge port (P11) of the second compression mechanism part (30) are open to the lower surface of the lid part (25b) of the middle plate (25).

  As shown in FIG. 4 (B), the first suction port (P1) and the first discharge port (P11) of each compression mechanism (20, 30) are circular in communication with the outermost fluid chamber (23d, 33d). Is the opening. In the figure, the first suction port (P1) is arranged on the right side of the blade (24, 34) and communicates with the low pressure chamber (23dL, 33dL) of the outermost fluid chamber (23d, 33d). Further, in the figure, the first discharge port (P11) is disposed on the left side of the blade (24, 34) and communicates with the high pressure chamber (23dH, 33dH) of the outermost fluid chamber (23d, 33d).

  As shown in FIG. 2, in each compression mechanism (20, 30), the second suction port (P2), the third suction port (P3), the second discharge port (P12), the third discharge port (P13), The fourth discharge port (P14) is formed in the cylinder (21, 31). These ports (P2, P3, P12, P13, P14) are opened in the back of each cylinder (21, 31). That is, in FIG. 2, the ports (P2, P3, P12, P13, P14) are opened on the upper surface of the first cylinder (21), and the ports (P2, P3, P12, P13, P) are opened on the lower surface of the second cylinder (31). P14) is open.

  As shown in FIG. 4A, the second suction port (P2) of each compression mechanism (20, 30) communicates with both the outer fluid chamber (23c, 33c) and the inner fluid chamber (23b, 33b). It is an oval opening. In the drawing, the second suction port (P2) is arranged on the right side of the blade (24, 34), and the low pressure chamber (23cL, 33cL) and the inner fluid chamber (23b, 33b) of the outer fluid chamber (23c, 33c). It communicates with the low pressure chamber (23bL, 33bL).

  As shown in FIG. 4A, the second discharge port (P12) of each compression mechanism (20, 30) is a circular opening communicating with the outer fluid chamber (23c, 33c). In the drawing, the second discharge port (P12) is disposed on the left side of the blade (24, 34) and communicates with the high pressure chamber (23cH, 33cH) of the outer fluid chamber (23c, 33c). As shown in the figure, the third discharge port (P13) of each compression mechanism (20, 30) is a circular opening communicating with the inner fluid chamber (23b, 33b). In the drawing, the third discharge port (P13) is disposed on the left side of the blade (24, 34) and communicates with the high pressure chamber (23bH, 33bH) of the inner fluid chamber (23b, 33b).

  As shown in FIG. 4 (A), the third suction port (P3) and the fourth discharge port (P14) of each compression mechanism (20, 30) are circular in communication with the innermost fluid chamber (23a, 33a). Is the opening. In the drawing, the third suction port (P3) is disposed on the right side of the blade (24, 34) and communicates with the low pressure chambers (23aL, 33aL) of the innermost fluid chambers (23a, 33a). Further, in the drawing, the fourth discharge port (P14) is arranged on the left side of the blade (24, 34) and communicates with the high pressure chamber (23aH, 33aH) of the innermost fluid chamber (23a, 33a).

  In FIG. 2, a discharge valve (88) for opening and closing the first discharge port (P11) of the first compression mechanism section (20) is provided on the upper surface of the body section (25a) of the middle plate (25). A discharge valve (88) for opening and closing the first discharge port (P11) of the second compression mechanism (30) is provided on the lower surface of the lid (25b) of the middle plate (25). In the same figure, on the back of each cylinder (21, 31), there is a discharge valve (88) for opening and closing the second discharge port (P12) and a discharge for opening and closing the third discharge port (P13). A valve (88) and a discharge valve (88) for opening and closing the fourth discharge port (P14) are provided. These discharge valves (88) are all reed valves.

<Suction channel>
In the compression mechanism (40), suction passages (71 to 74) for guiding the suction pipes (61 to 64) to the fluid chambers (23a to 23d, 33a to 33d) are formed. These suction passages (71 to 74) do not cross each other, and other parts formed in the compression mechanism (40) (each blade (24, 34), discharge valve (88), etc.) Is formed in the compression mechanism (40) so as not to interfere.

  The first suction channel (71) is formed in the middle plate (25), and connects the first suction pipe (61) to the first suction ports (P1, P1) of the compression mechanism parts (20, 30). The second suction channel (72) is formed in the rear head (19), and connects the second suction pipe (62) to the second suction port (P2) of the second compression mechanism (30). The third suction channel (73) is formed in the front head (16), and connects the third suction pipe (63) to the second suction port (P2) of the first compression mechanism section (20).

  The fourth suction channel (74) is formed across the middle plate (25), both cylinders (21, 31), the front head (16), and the rear head (19). It connects with the 4th suction port (P4, P4) of each compression mechanism part (20, 30). The fourth suction flow path (74) includes a suction pipe side flow path (74a) extending vertically in the compression mechanism (40) and a suction port side flow path (74b) extending horizontally in the compression mechanism (40). ) And are formed. The suction port side flow path (74b) is formed by cutting out the lower surface of the flat plate portion (16a) of the front head (16) in FIG. 2 and the upper surface of the flat plate portion (19a) of the rear head (19) in FIG. Therefore, it can be formed easily.

<Discharge flow path>
The compression mechanism (40) is formed with discharge channels (81 to 84) for leading the refrigerant compressed in the fluid chambers (23a to 23d, 33a to 33d) from the compression mechanism (40). These discharge flow paths (81 to 84) do not cross each other and other parts formed in the compression mechanism (40) (each blade (24, 34), discharge valve (88), etc.) Is formed in the compression mechanism (40) so as not to interfere.

  The first discharge channel (81) is formed in the middle plate (25), and connects the first discharge ports (P11, P11) of the compression mechanism parts (20, 30) to the first discharge pipe (66). The second discharge channel (82) is formed in the rear head (19), and the second discharge port (P12) and the third discharge port (P13) of the second compression mechanism (30) are connected to the second discharge pipe (67). Connect to. The third discharge channel (83) is formed in the front head (16), and the second discharge port (P12) and the third discharge port (P13) of the first compression mechanism (20) are connected to the third discharge pipe (68). ).

  One fourth discharge channel (84) is formed in each of the front head (16) and the rear head (19). The fourth discharge channel (84) of the front head (16) connects the fourth suction port (P4) of the first compression mechanism (20) to the muffler space (27a). The fourth discharge flow path (84) of the rear head (19) communicates with the fourth suction port (P4) of the second compression mechanism (30) and enters the muffler space (27a) via the gas outlet passage (29). Connecting.

  The gas outlet passage (29) is formed by an upstream passage portion (29a) extending horizontally in the compression mechanism (40) and a downstream passage portion (29b) extending vertically in the compression mechanism (40). Yes. The upstream passage portion (29a) can be easily formed by cutting out the upper surface of the flat plate portion (19a) of the rear head (19) in FIG.

<Relief mechanism>
The compression mechanism (40) is provided with a relief mechanism (100). The relief mechanism (100) includes a relief port (101) and a relief valve (102). The relief port (101) is formed in the front head (16), and connects the third discharge passage (83) and the muffler space (27a). The relief valve (102) is a reed valve that opens and closes the relief port (101). The relief valve (102) is installed on the upper surface of the front head (16) in FIG.

<Pressing mechanism>
Each compression mechanism part (20, 30) of the compression mechanism (40) is provided with a pressing mechanism (90) for pressing the piston (22, 32) against the cylinder (21, 31). The pressing mechanism (90) applies the pressure of the gas refrigerant to the back surface (22k, 32k) of the end plate portion (22g, 32g) of the piston (22, 32), thereby moving the piston (22, 32) to the cylinder (21, Press to 31).

  The pressing mechanism (90) of each compression mechanism portion (20, 30) includes a first seal ring (91) having a small diameter, and a second seal ring (92) having a large diameter surrounding the first seal ring (91). It has. The first seal ring (91) and the second seal ring (92) constituting the pressing mechanism (90) of the first compression mechanism (20) are the upper surface of the main body (25a) of the middle plate (25) in FIG. And is in sliding contact with the back surface (22k) of the end plate portion (22g) of the first piston (22). The first seal ring (91) and the second seal ring (92) constituting the pressing mechanism (90) of the second compression mechanism section (30) are the lower surface of the lid portion (25b) of the middle plate (25) in FIG. And is in sliding contact with the back surface (32k) of the end plate portion (32g) of the second piston (32).

  The pressing mechanism (90) of each compression mechanism (20, 30) includes an annular groove (93a, 93b) and an intermediate pressure introduction path (96a, 96b). In the pressing mechanism (90) of the first compression mechanism part (20), the first annular groove (93a) is provided with the first seal ring (91) and the second seal ring on the upper surface of the body part (25a) of the middle plate (25). (92), the first intermediate pressure introduction passage (96a) connects the first annular groove (93a) to the fourth suction passage (74). In the pressing mechanism (90) of the second compression mechanism part (30), the second annular groove (93b) is provided with the first seal ring (91) and the second seal ring on the lower surface of the lid part (25b) of the middle plate (25). (92), and the second intermediate pressure introduction passage (96b) connects the second annular groove (93b) to the first discharge passage (81).

-Configuration as a four-stage compressor-
The compressor (1) of the present reference technology is a four-stage compressor that compresses refrigerant into four stages in the compression mechanism (40).

  The first discharge pipe (66) is connected to the second suction pipe (62) via a cooler for cooling the refrigerant. The second discharge pipe (67) is connected to the third suction pipe (63) via a cooler for cooling the refrigerant. An injection pipe for introducing intermediate pressure refrigerant is connected between the second discharge pipe (67) and the third suction pipe (63). The third discharge pipe (68) is connected to the fourth suction pipe (64) via a cooler for cooling the refrigerant. In addition, illustration of these coolers and injection piping is abbreviate | omitted.

-Driving action-
The operation of the compressor (1) will be described. During the operation of the compressor (1), the electric motor (50) drives the compression mechanism (40).

<Operation of compression mechanism>
The first compression mechanism section (20) and the second compression mechanism section (30) perform the same operation. However, the operation of the first compression mechanism (20) and the operation of the second compression mechanism (30) are out of phase with each other by 180 °.

  In the first compression mechanism portion (20), the first piston (22) is driven by the first eccentric portion (53a) of the drive shaft (53). The first piston (22) swings with the center point of the bush portion (24c) as the swing center, and moves forward and backward in the longitudinal direction of the first blade (24) together with the first blade (24). In the first compression mechanism section (20), the first piston (22) revolves while swinging with respect to the first cylinder (21), and the four fluid chambers (23a) of the first compression mechanism section (20) are obtained. , 23b, 23c, 23d), the refrigerant is sucked and compressed.

  In the innermost fluid chamber (23a) and the outer fluid chamber (23c), the drive shaft (53) rotates in the clockwise direction in FIG. 11 (A) from the state of FIG. 11 (A), and FIGS. As the state changes, the volume of the low pressure chamber (23aL, 23cL) increases, and the refrigerant is sucked into the low pressure chamber (23aL, 23cL) from the suction port (P3, P2). Further, when the drive shaft (53) makes one revolution and again enters the state of FIG. 11 (A), the suction of the refrigerant into the low pressure chambers (23aL, 23cL) is completed. The low-pressure chamber (23aL, 23cL) becomes a high-pressure chamber (23aH, 23cH) in which the refrigerant is compressed, and a new low-pressure chamber (23aL, 23cL) is formed across the first blade (24).

  When the drive shaft (53) further rotates, in the innermost fluid chamber (23a) and the outer fluid chamber (23c), the refrigerant is sucked into the low pressure chamber (23aL, 23cL), while the volume of the high pressure chamber (23aH, 23cH) Decreases and the refrigerant in the high-pressure chamber (23aH, 23cH) is compressed. When the pressure in the high pressure chamber (23aH) of the innermost fluid chamber (23a) exceeds the pressure in the fourth discharge passage (84), the discharge valve (88) is opened, and the fourth discharge passage (from the high pressure chamber (23aH)) 84) The refrigerant is discharged. When the pressure in the high pressure chamber (23cH) of the outer fluid chamber (23c) exceeds the pressure in the third discharge passage (83), the discharge valve (88) opens, and the third discharge passage (83) is opened from the high pressure chamber (23cH). ) Is discharged.

  In the inner fluid chamber (23b), the drive shaft (53) rotates clockwise from the state shown in FIG. 11C to change to the state shown in FIGS. 11D to 11B. The volume of the low pressure chamber (23bL) increases, and the refrigerant is sucked into the low pressure chamber (23bL) from the suction port (P2). Further, when the drive shaft (53) makes one revolution and again enters the state of FIG. 11 (C), the suction of the refrigerant into the low pressure chamber (23bL) is completed. The low pressure chamber (23bL) becomes a high pressure chamber (23bH) in which the refrigerant is compressed, and a new low pressure chamber (23bL) is formed across the first blade (24).

  When the drive shaft (53) further rotates, in the inner fluid chamber (23b), the refrigerant is sucked into the low pressure chamber (23bL), while the volume of the high pressure chamber (23bH) decreases, and the refrigerant in the high pressure chamber (23bH) Is compressed. When the pressure in the high pressure chamber (23bH) exceeds the pressure in the third discharge channel (83), the discharge valve (88) opens, and the refrigerant is discharged from the high pressure chamber (23bH) to the third discharge passage (83). The

  In the outermost fluid chamber (23d), the drive shaft (53) rotates clockwise from the state of FIG. 12 (A) to change to the states of FIG. 12 (B) to FIG. 12 (D). Accordingly, the volume of the low pressure chamber (23dL) increases, and the refrigerant is sucked into the low pressure chamber (23dL) from the suction port (P1). Further, when the drive shaft (53) makes one revolution and again enters the state of FIG. 12 (A), the suction of the refrigerant into the low pressure chamber (23dL) is completed. The low pressure chamber (23dL) becomes a high pressure chamber (23dH) in which the refrigerant is compressed, and a new low pressure chamber (23dL) is formed across the first blade (24).

  When the drive shaft (53) further rotates, in the outermost fluid chamber (23d), the refrigerant is sucked into the low-pressure chamber (23dL), while the volume of the high-pressure chamber (23dH) decreases, and the inside of the high-pressure chamber (23dH) The refrigerant is compressed. When the pressure in the high pressure chamber (23dH) exceeds the pressure in the first discharge channel (81), the discharge valve (88) opens, and the refrigerant is discharged from the high pressure chamber (23dH) to the first discharge channel (81). The

  In the second compression mechanism part (30), the second piston (32) is driven by the second eccentric part (53b) of the drive shaft (53). The second piston (32) swings about the center point of the bush portion (34c) as the swing center, and moves forward and backward in the longitudinal direction of the second blade (34) together with the second blade (34). In the second compression mechanism section (30), the second piston (32) revolves while swinging relative to the second cylinder (31), and the four fluid chambers (33a) of the second compression mechanism section (30) are revolved. , 33b, 33c, 33d), the refrigerant is sucked and compressed.

<Compressor four-stage compression operation>
As described above, the compressor (1) of the present reference technology is a four-stage compressor.

  The low-pressure refrigerant that has flowed out of the evaporator of the refrigerant circuit flows into the first suction passage (71) through the first suction pipe (61). Part of the refrigerant flowing into the first suction passage (71) is sucked into the low pressure chamber (23dL) of the outermost fluid chamber (23d) of the first compression mechanism (20), and the rest is the second compression mechanism. It is sucked into the low pressure chamber (33dL) of the outermost fluid chamber (33d) of (30).

  The refrigerant discharged from the high pressure chamber (23dH, 33dH) of the outermost fluid chamber (23d, 33d) of each compression mechanism (20, 30) to the first discharge passage (81) is connected to the first discharge pipe (66). It flows into the second suction passage (72) through the second suction pipe (62) in order. A part of the refrigerant flowing into the second suction passage (72) is sucked into the low pressure chamber (33cL) of the outer fluid chamber (33c) of the second compression mechanism portion (30), and the remaining is the second compression mechanism portion ( 30) is sucked into the low pressure chamber (33bL) of the inner fluid chamber (33b).

  The refrigerant discharged from the outer fluid chamber (33c) of the second compression mechanism (30) and the high pressure chamber (33cH, 33bH) of the inner fluid chamber (33b) to the second discharge passage (82) is supplied to the second discharge pipe ( 67) and the third suction pipe (63) in order, and flows into the third suction passage (73). A part of the refrigerant flowing into the third suction passage (73) is sucked into the low pressure chamber (23cL) of the outer fluid chamber (23c) of the first compression mechanism portion (20), and the remaining is the first compression mechanism portion ( 20) is sucked into the low pressure chamber (23bL) of the inner fluid chamber (23b).

  The refrigerant discharged from the outer fluid chamber (23c) of the first compression mechanism (20) and the high pressure chambers (23cH, 23bH) of the inner fluid chamber (23b) to the third discharge passage (83) is supplied to the third discharge pipe ( 68) and the fourth suction pipe (64) in order, and flows into the fourth suction passage (74). A part of the refrigerant flowing into the fourth suction passage (74) is sucked into the low pressure chamber (23aL) of the innermost fluid chamber (23a) of the first compression mechanism portion (20), and the rest is the second compression mechanism portion. It is sucked into the low pressure chamber (33adL) of the innermost fluid chamber (33a) of (30).

  The refrigerant discharged from the high pressure chamber (23aH, 33aH) of the innermost fluid chamber (23a, 33a) of each compression mechanism (20, 30) to the fourth discharge passage (84) passes through the muffler space (27a). Then, it flows out of the casing (10) through the fourth discharge pipe (69) provided at the top of the casing (10).

<Discharged refrigerant from inner fluid chamber and outer fluid chamber>
As described above, the inner fluid chamber (23b) and the outer fluid chamber (23c) of the first compression mechanism section (20) suck in the refrigerant from the third suction passage (73) and enter the third discharge passage (83). Is discharged. The inner fluid chamber (33b) and the outer fluid chamber (33c) of the second compression mechanism section (30) suck in the refrigerant from the second suction passage (72) and discharge the refrigerant into the second discharge passage (82). .

  On the other hand, in each compression mechanism (20, 30), the refrigerant is sucked into the inner fluid chamber (23b, 33b) and discharged after compression, and the refrigerant is sucked into the outer fluid chamber (23c, 33c) and compressed. Each phase is 180 degrees out of phase with the operation to be discharged later. Therefore, in the first compression mechanism section (20), the refrigerant compressed in the inner fluid chamber (23b) and the refrigerant compressed in the outer fluid chamber (23c) each time the drive shaft (53) rotates 180 °. Are alternately discharged into the third discharge passage (83). In the second compression mechanism section (30), the refrigerant compressed in the inner fluid chamber (33b) and the refrigerant compressed in the outer fluid chamber (33c) each time the drive shaft (53) rotates by 180 ° Are alternately discharged into the second discharge passage (82).

  In each compression mechanism (20, 30), the volume of the inner fluid chamber (23b, 33b) is equal to the volume of the outer fluid chamber (23c, 33c). For this reason, in the 1st compression mechanism part (20), whenever the drive shaft (53) rotates 180 degrees, the refrigerant | coolant of the same mass is discharged from an inner side fluid chamber (23b) or an outer side fluid chamber (23c). In the second compression mechanism section (30), the same mass of refrigerant is discharged from the inner fluid chamber (33b) or the outer fluid chamber (33c) every time the drive shaft (53) rotates 180 °.

-Effects of Reference Technology 1-
As described above, in the first compression mechanism section (20), the inner fluid chamber (23b) and the outer fluid chamber (23c) alternately discharge refrigerant to the third discharge passage (83), and the second compression mechanism section ( In 30), the inner fluid chamber (33b) and the outer fluid chamber (33c) alternately discharge the refrigerant into the second discharge passage (82).

  When the volume of the inner fluid chamber is smaller than the volume of the outer fluid chamber as in the conventional rotary compressor, different mass refrigerants are discharged from the inner fluid chamber and the outer fluid chamber at different timings. For this reason, in the conventional rotary compressor, the flow and pressure of the refrigerant in the second discharge passage and the third discharge passage fluctuate in a complicated manner, and vibrations and noises resulting therefrom may become a problem.

On the other hand, the piston (22, 32) of each compression mechanism part (20, 30) of this reference technology is “the distance H from the intermediate front face part (22h) to the protruding end face (22d) of the outer piston part (22c)”. _{2 ""} is longer than the distance H _{3 "of} the outer front portion from (22i) to the protruding end surface of the outer piston portion (22c) (22d). As a result, in each compression mechanism part (20, 30) of this reference technique , the volume of the inner fluid chamber (23b, 33b) is equal to the volume of the outer fluid chamber (23c, 33c).

For this reason, in each compression mechanism part (20, 30) of this reference technology , the mass of the refrigerant discharged from the inner fluid chamber (23b, 33b) and the mass of the refrigerant discharged from the outer fluid chamber (23c, 33c) Are substantially equal. Therefore, according to the present reference technique , it is possible to suppress fluctuations in the flow and pressure of the refrigerant in the second discharge passage (82) and the third discharge passage (83), and to reduce vibration and noise caused thereby.

Embodiment 1 of the Invention
A first embodiment of the present invention will be described. The compressor (1) of the present embodiment is different from the compressor (1) of Reference Technology 1 in the configuration of the blades (24, 34).

As shown in FIG. 13, the blades (24, 34) of the compression mechanism portions (20, 30) of the present embodiment have first portions (24h, 34h) in which bush portions (24c, 34c) are arranged coaxially. ) and a second portion (24i, that is composed by a 34i).

The first part (24h, 34h), the height of a cylindrical portion of the W _5, the proximal side plate portion (24a, 34a) of the elongated portion (24d, 34d) and a distal side plate portions (24b, 34b ). The first part (24h, 34h) height W ₅ of the elongated part (24d, 34d) substantially equal to the length W ₁ of the short side of the. In FIG. 13, the first portion (24h, 34h) has an upper end surface that is flush with the upper surface of the long portion (24d, 34d), and a lower end surface that is the lower surface of the long portion (24d, 34d). Form the same plane.

The second portion (24i, 34i) is height W ₆ of the cylindrical (or disk shape) a portion of the first part (24h, 34h) are formed separately. In FIG. 13, the second part (24i, 34i) is disposed below the first part (24h, 34h). The first part (24h, 34h) of the height W ₅ second portion (24i, 34i) is the sum of the height W ₆ of the bushing portion (24c, 34c) the height W ₃ substantially equal to (W _{3 = W 5 + W 6)} .

<< Reference Technology 2 >>
Reference technique 2 of the present invention will be described. The compressor (1) of the present embodiment is obtained by changing the configuration of the compression mechanism (40) of the compressor (1) of Reference Technique 1 . Here, the difference between the compression mechanism (40) of the present embodiment and the compression mechanism (40) of Reference Technique 1 will be described.

As shown in FIGS. 14 and 15, the compression mechanism (40) of the present embodiment includes a piston (22, 32), a cylinder (21, 31), and a blade (24, 34) of each compression mechanism (20, 30). ) Is different from the compression mechanism (40) of Reference Technique 1 .

<Piston and cylinder>
Regarding the piston (22, 32) and the cylinder (21, 31) of the present embodiment, differences from the piston (22, 32) and the cylinder (21, 31) of the reference technique 1 will be described. In the present embodiment, the first piston (22) and the second piston (32) are members having the same shape, and the first cylinder (21) and the second cylinder (31) are members having the same shape.

As shown in FIG. 16 (B), the piston (22, 32) has a distance H ₁ from the intermediate front surface portion (22h, 32h) to the protruding end surface (22b, 32b) of the inner piston portion (22a, 32a) (ie, , The height of the inner piston part (22a, 32a) is a distance H ₂ from the intermediate front part (22h, 32h) to the projecting end face (22d, 32d) of the outer piston part (22c, 32c) (ie, the outer piston Part (22c, 32c) height). Further, the piston (22, 32) is intermediate the front portion (22h, 32h) outer piston portion from (22c, 32c) protruding end surfaces of the (22 d, 32d) is a distance of H ₂ up to the outer front face (22i, 32i) the outer piston portion from (22c, 32c) longer than the distance H ₃ to the protruding end surfaces of (22d, 32d). This is the same as the piston (22, 32) of Reference Technique 1 .

As shown in FIG. 16A, the cylinder (21, 31) has a distance L ₁ from the intermediate sliding contact surface (21e, 31e) to the bottom wall surface (21i, 31i) of the inner recess (21g, 31g) (ie, , The depth of the inner recess (21g, 31g) is the distance L ₂ from the intermediate sliding contact surface (21e, 31e) to the bottom wall surface (21p, 31p) of the outer recess (21k, 31k) (ie, the outer recess ( Longer than the depth of 21k, 31k). Further, the cylinder (21, 31), an intermediate sliding surface (21e, 31e) from the outer recesses (21k, 31k) bottom wall surface (21p, 31p) of the distance L ₂ to the outer sliding surface (21f, 31f ) from the outer recesses (21k, the bottom wall surface (21p of 31k), longer than the distance L ₃ to 31p). This is the same as the cylinder (21, 31) of Reference Technique 1 .

As shown in FIGS. 17 and 18, the guide groove (21r, 31r) formed in the cylinder (21, 31) is recessed from the bottom wall surface (21p, 31p) of the outer recess (21k, 31k). In the cylinder (21, 31), the bottom wall surface (21s, 31s) of the guide groove from the intermediate sliding surface (21e, 31e) (21r, 31r) is the distance L ₅ to, the intermediate sliding surface (21e, 31e) bottom wall surface (21i, 31i) of the inner recess (21g, 31g) equal to the distance L ₁ to. That is, the bottom wall surface (21s, 31s) of the guide groove (21r, 31r) and the bottom wall surface (21i, 31i) of the inner recess (21g, 31g) form the same plane. Further, the bottom wall surface (21s, 31s) of the guide groove from the intermediate sliding surface (21e, 31e) (21r, 31r) is the distance L ₅ to the intermediate slide surface (21e, 31e) from the outer recesses (21k, 31k bottom wall surface (21p) of longer than the distance L ₂ to 31p).

As shown in FIG. 14, in each compression mechanism (20, 30) of the present embodiment, the piston (22, 32) and the cylinder (21, 31) are used to form the innermost fluid chamber (23a) in the same manner as in Reference Technique 1. 33a), inner fluid chambers (23b, 33b), outer fluid chambers (23c, 33c), and outermost fluid chambers (23d, 33d). On the other hand, the piston (22, 32) of this embodiment, the intermediate front portion (22h, 32h) protruding end surface of the inner piston portion from (22a, 32a) (22b, 32 b) the distance H ₁ to the intermediate front portion ( 22h, outer piston part from 32h) (22c, end surfaces of 32c) (22d, longer than the distance of H ₂ up to 32d). Further, the cylinder (21, 31) of this embodiment, the bottom wall surface (21i, 31i) of the inner recess from the intermediate sliding surface (21e, 31e) (21g, 31 g) is the distance L ₁ to the intermediate sliding surface (21e, 31e) from the outer recesses (21k, 31k) bottom wall surface (21p, 31p) of longer than the distance L ₂ to. For this reason, the volume of the innermost fluid chamber (23a, 33a) of each compression mechanism portion (20, 30) of the present embodiment is equal to the innermost fluid chamber (23a) of each compression mechanism portion (20, 30) of Reference Technique 1. , 33a).

<blade>
Regarding the blade (24, 34) of the present embodiment, differences from the blade (24, 34) of the reference technique 1 will be described. In the present embodiment, the first blade (24) and the second blade (34) are members having the same shape.

As shown in FIG. 19, the blade of the present embodiment (24, 34) is proximal the side plate portions (24a, 34a) the elongated portion of (24d, 34d) length W ₁ of the short side of the reference technique 1 extending portions (24d, 34d) greater than the tip side plate portions (24b, 34b) distal side plate portion length W ₄ of the reference technique 1 of the short side of (24b, 34b) longer than. The height W ₃ of the bushing portion of the present embodiment (24c, 34c) is the same as the height of the bushing portion of the reference technology 1 (24c, 34c). In other words, the blade of the present embodiment (24, 34), the tip side plate portions (24b, 34b) the length W ₄ bush portion of the short side of (24c, 34c) longer than the height W ₃ of the. Accordingly, in FIG. 19, the upper surface of the long portion (24d, 34d) and the upper surface of the distal end side plate portion (24b, 34b) are positioned above the upper end surface of the bush portion (24c, 34c).

  In FIG. 19, the long part (24d, 34d) is such that the upper part of the upper end surface of the bush part (24c, 34c) extends along the upper end surface of the bush part (24c, 34c). 34b). In the blade (24, 34) shown in FIG. 19, the upper surface of the long portion (24d, 34d) and the upper surface of the tip side plate portion (24b, 34b) form the same plane. In the blade (24, 34) of the present embodiment, the portion protruding from the bush portion (24c, 34c) is the bottom wall surface (21p, 31p) of the outer recess (21k, 31k) in the guide groove (21r, 31r). Fits into the recessed part more slidably.

Also in each compression mechanism part (20, 30) of this embodiment, a braid | blade (24, 34) has innermost fluid chamber (23a, 33a), inner fluid chamber (23b, 33b), and outer fluid chamber (23c, 33c). ) And the outermost fluid chamber (23d, 33d) are divided into a high pressure chamber and a low pressure chamber. As described above, the blade (24, 34) is fitted into a portion of the guide groove (21r, 31r) that is recessed from the bottom wall surface (21p, 31p) of the outer recess (21k, 31k). Therefore, the cylinder (21, 31) inside the recess in (21g, 31 g) depth L ₁ is outside recess (21k, 31k) compression mechanism of the long present embodiment than the depth L ₂ (20, 30) In this case, the innermost fluid chamber (23a, 33a), the inner fluid chamber (23b, 33b), and the outer fluid chamber (23c, 33c) are partitioned by one blade (24, 34).

-Effect of Reference Technology 2-
In the present embodiment, the piston (22, 32) of the compressor (1) has a “distance H ₁ from the intermediate front surface portion (22h, 32h) to the protruding end surface (22b, 32b) of the inner piston portion (22a, 32a). "Is longer than the" distance H ₂ from the intermediate front surface portion (22h, 32h) to the protruding end surface (22d, 32d) of the outer piston portion (22c, 32c) ". Therefore, by adjusting the “distance H ₁ from the intermediate front surface portion (22h, 32h) to the protruding end surface (22b, 32b) of the inner piston portion (22a, 32a)”, the inner fluid chamber (23b, 33b) The volume of the innermost fluid chamber (23a, 33a) can be freely set without being restricted by the volume and the volume of the outer fluid chamber (23c, 33c). Therefore, according to the present embodiment, it is possible to appropriately set the volume of the innermost fluid chamber (23a, 33a), and the performance of the compressor (1) can be improved.

  As described above, the compressor (1) of the present embodiment constitutes a four-stage compressor. The innermost fluid chamber (23a, 33a) of each compression mechanism (20, 30) is the fourth (ie, the highest) fluid chamber.

Here, the inner piston portion (22a, 32a) of a height H ₁ is used as the outer piston portion (22c, 32c) of height between H ₂ equal similar four-stage compressor and the embodiment of conventional compressor In this case, the volume of the innermost fluid chamber (23a, 33a) cannot be secured sufficiently, the compression ratio of the fourth stage becomes smaller than the compression ratio from the first stage to the third stage, and the compression ratio of each stage is approximately It was difficult to perform equal ideal four-stage compression.

In contrast, in the compressor of the present embodiment (1), since the inner piston section (22a, 32a) of a height H ₁ is greater than the height H ₂ of the outer piston portion (22c, 32c), the innermost fluid It is possible to secure a sufficient volume of the chambers (23a, 33a). Thus, using the compressor of the present embodiment (1) as four-stage compressor, by appropriately setting the height H ₁ of the inner piston section (22a, 32a), an ideal compression ratio of each stage is approximately equal Four-stage compression can be realized.

  In the compressor (1) of the present embodiment, the guide grooves (21r, 31r) into which the blades (24, 34) are fitted are formed in the cylinder (21, 31). This cylinder (21, 31) has a distance from the intermediate sliding contact surface (21e, 31e) to the bottom wall surface (21s, 31s) of the guide groove (21r, 31r). It is equal to the distance to the bottom wall surface (21i, 31i) of the recess (21g, 31g). Therefore, the distance from the intermediate sliding contact surface (21e, 31e) to the bottom wall surface is reduced by the inner recess (21g, 31g) by the blade (24, 34) that divides the innermost fluid chamber (23a, 33a) into the low pressure chamber and the high pressure chamber. The inner fluid chambers (23b, 33b) and the outer fluid chambers (23c, 33c) formed in the outer recesses (21k, 31k) shorter than () can also be partitioned into a low pressure chamber and a high pressure chamber.

<< Embodiment 2 of the Invention >>
A second embodiment of the present invention will be described. The compressor (1) of the present embodiment is different from the compressor (1) of Reference Technology 2 in the configuration of the blades (24, 34).

As in the first embodiment, the blades (24, 34) of the compression mechanism portions (20, 30) of the present embodiment have first portions (24h, 34h) in which the bush portions (24c, 34c) are arranged coaxially. ) And the second portion (24i, 34i).

As shown in FIG. 20, in the blade (24, 34) of the present embodiment, the first portion (24h, 34h) is the long portion (24d, 34d) of the proximal end side plate portion (24a, 34a) and the distal end side plate portion. (24b, 34b) and the second part (24i, 34i) are formed separately from the first part (24h, 34h). The first part (24h, 34h) of the height W ₅ second portion (24i, 34i) is the sum of the height W ₆ of the bushing portion (24c, 34c) equal to the height W ₃ substantially _{(W 3 = W 5 + W} 6).

<< Embodiment 3 of the Invention >>
Embodiment 3 of the present invention will be described. The compressor (1) of this embodiment is a three-stage compressor that compresses refrigerant in three stages in the compression mechanism (40). Here, the difference between the compressor (1) of the present embodiment and the compressor (1) of the first embodiment will be described.

  As shown in FIG. 21, the outermost cylinder part (21c, 31c) of each cylinder (21, 31) of this embodiment has an inner peripheral surface of the end plate part (22g, 32g) of the piston (22, 32). No contact with the outer surface. For this reason, in each compression mechanism part (20, 30), the space formed between the end plate part (22g, 32g) and the outermost cylinder part (21c, 31c) of the piston (22, 32) compresses the refrigerant. It becomes an invalid space (23e, 33e) that does not. For this reason, in the compression mechanism (40) of the present embodiment, the first suction passage (71) and the first discharge passage (81) of the first embodiment are not formed in the middle plate (25). Further, the compressor (1) of the present embodiment is not provided with the first suction pipe (61) and the first discharge pipe (66) of the first embodiment.

  The middle plate (25) of the embodiment is composed of one member. In the compression mechanism (40) of the present embodiment, the first annular groove (93a) is formed on the upper surface of the middle plate (25), and the second annular groove (92b) is formed on the lower surface of the middle plate (25). The first annular groove (93a) and the second annular groove (92b) communicate with the fourth suction passage (74) via an intermediate pressure introduction passage (96c) formed in the middle plate (25).

  The second discharge pipe (67) is connected to the third suction pipe (63) via a cooler for cooling the refrigerant. An injection pipe for introducing intermediate pressure refrigerant is connected between the second discharge pipe (67) and the third suction pipe (63). The third discharge pipe (68) is connected to the fourth suction pipe (64) via a cooler for cooling the refrigerant. In addition, illustration of these coolers and injection piping is abbreviate | omitted.

  As described above, the compressor (1) of the present embodiment is a three-stage compressor.

  The low-pressure refrigerant that has flowed out of the evaporator of the refrigerant circuit flows into the second suction passage (72). A part of the refrigerant flowing into the second suction passage (72) is sucked into the low pressure chamber (33cL) of the outer fluid chamber (33c) of the second compression mechanism portion (30), and the remaining is the second compression mechanism portion ( 30) is sucked into the low pressure chamber (33bL) of the inner fluid chamber (33b).

  The refrigerant discharged from the outer fluid chamber (33c) of the second compression mechanism (30) and the high pressure chamber (33cH, 33bH) of the inner fluid chamber (33b) to the second discharge passage (82) is supplied to the second discharge pipe ( 67) and the third suction pipe (63) in order, and flows into the third suction passage (73). A part of the refrigerant flowing into the third suction passage (73) is sucked into the low pressure chamber (23cL) of the outer fluid chamber (23c) of the first compression mechanism portion (20), and the remaining is the first compression mechanism portion ( 20) is sucked into the low pressure chamber (23bL) of the inner fluid chamber (23b).

  The refrigerant discharged from the outer fluid chamber (23c) of the first compression mechanism (20) and the high pressure chambers (23cH, 23bH) of the inner fluid chamber (23b) to the third discharge passage (83) is supplied to the third discharge pipe ( 68) and the fourth suction pipe (64) in order, and flows into the fourth suction passage (74). A part of the refrigerant flowing into the fourth suction passage (74) is sucked into the low pressure chamber (23aL) of the innermost fluid chamber (23a) of the first compression mechanism portion (20), and the rest is the second compression mechanism portion. It is sucked into the low pressure chamber (33adL) of the innermost fluid chamber (33a) of (30).

  The refrigerant discharged from the high pressure chamber (23aH, 33aH) of the innermost fluid chamber (23a, 33a) of each compression mechanism (20, 30) to the fourth discharge passage (84) passes through the muffler space (27a). Then, it flows out of the casing (10) through the fourth discharge pipe (69) provided at the top of the casing (10).

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

  For example, in the first and second embodiments, the four-stage compression mechanism has been described, and in the third embodiment, the three-stage compression mechanism has been described. The compressor (1) provided with (40) is applicable.

  In each of the above embodiments, the volume of the inner fluid chamber (23b) of the first compression mechanism (20) is the same as the volume of the inner fluid chamber (33b) of the second compression mechanism (30). However, the volumes of these fluid chambers (23b, 33b) are not necessarily the same. In the first and second embodiments, the volume of the outer fluid chamber (23c) of the first compression mechanism (20) is the same as the volume of the outer fluid chamber (33c) of the second compression mechanism (30). However, the volumes of these fluid chambers (23c, 33c) are not necessarily the same.

  As described above, the present invention is useful for a rotary compressor in which a plurality of fluid chambers are formed by a pair of pistons and cylinders.

1 Compressor
21 1st cylinder
21c Outermost cylinder part
21e Intermediate sliding contact surface
21g Inner recess
21h Side wall surface
21i Bottom wall
21k outer recess
21n outer wall
21r guide groove
21s Bottom wall
22 First piston
22a Inner piston
22b Tip surface
22c Outer piston part
22d Tip surface
22g End plate
22h Middle front
22i Front outside
23a Innermost fluid chamber
23b Inner fluid chamber
23c Outer fluid chamber
23d Outermost fluid chamber
24 First blade

Claims (5)

A cylinder (21) and a piston (22) that rotates eccentrically with respect to the cylinder (21) are provided, and fluid is sucked into a fluid chamber formed by the cylinder (21) and the piston (22) and compressed. A rotary compressor,
The piston (22)
A flat end plate (22g),
A cylindrical inner piston portion (22a) protruding from the front surface of the end plate portion (22g);
A cylindrical outer piston part (22c) projecting from the front face of the end plate part (22g) and surrounding the inner piston part (22a);
The cylinder (21)
An inner recess (21g) in which the inner piston portion (22a) fits in a circular recess, and an outer portion of the inner piston portion (22a) becomes the innermost fluid chamber (23a);
An annular recess into which the outer piston part (22c) is fitted, the inner part of the outer piston part (22c) becomes the inner fluid chamber (23b), and the outer part of the outer piston part (22c) is the outer part. While the outer recess (21k) that becomes the fluid chamber (23c) is formed,
A blade (24) that partitions the innermost fluid chamber (23a), the inner fluid chamber (23b), and the outer fluid chamber (23c) into a low-pressure chamber on the suction side and a high-pressure chamber on the discharge side;
The piston (22) extends from the intermediate front surface portion (22h), which is a portion between the inner piston portion (22a) and the outer piston portion (22c), of the front surface of the end plate portion (22g) to the outer piston portion (22h). The distance from the front end face (22d) of 22c) to the outer piston part (22c) from the outer front face part (22i), which is the outer side of the outer piston part (22c), of the front face of the end plate part (22g). ) rather than length than the distance to the end surfaces (22d) of,
The blade (24) includes a tip side plate (24b) that partitions the innermost fluid chamber (23a) and the inner fluid chamber (23b) into a suction-side low pressure chamber and a discharge-side high pressure chamber, and the outer fluid chamber ( 23c) a base plate (24a) that divides the low pressure chamber on the suction side and the high pressure chamber on the discharge side, and a columnar shape disposed between the top plate (24b) and the base plate (24a). A bush part (24c),
The outer piston part (22c) is partly divided in the circumferential direction, and the end face (C1, C2) of the parting part is a curved surface in sliding contact with the bush part (24c),
The bush portion (24c) includes a cylindrical first portion (24h) formed integrally with the distal end side plate portion (24b) and the proximal end side plate portion (24a), and the first portion (24h) The second portion (24i) formed in a separate cylindrical shape and disposed on one end face side of the first portion (24h),
The end surface of the first portion (24h) on the second portion (24i) side is flush with the sliding surface of the base end side plate portion (24a) with the outer front surface portion (22i) of the piston (22). A rotary compressor characterized by being formed . In claim 1,
The distance from the intermediate front surface portion (22h) to the protruding end surface (22d) of the outer piston portion (22c) is such that the volume of the inner fluid chamber (23b) is equal to the volume of the outer fluid chamber (23c). A rotary compressor characterized by being set. In claim 1 or 2,
The piston (22) has a distance from the intermediate front surface portion (22h) to the protruding end surface (22b) of the inner piston portion (22a) so that the protruding end of the outer piston portion (22c) extends from the intermediate front surface portion (22h). A rotary compressor characterized by being longer than the distance to the surface (22d). In claim 3,
The cylinder (21) extends in the radial direction of the cylinder (21) from the side wall surface (21h) of the inner recess (21g) to the outer side of the outer wall surface (21n) of the outer recess (21k). 24) A guide groove (21r) is slidably fitted,
The cylinder (21) is located between the inner recess (21g) and the outer recess (21k), and is an intermediate sliding contact surface (21e) that is in sliding contact with the front surface of the end plate portion (22g) of the piston (22). The distance from the guide groove (21r) to the bottom wall surface (21s) is equal to the distance from the intermediate sliding contact surface (21e) to the bottom wall surface (21i) of the inner recess (21g) Type compressor. In any one of Claims 1 thru | or 4,
The cylinder (21) includes an outermost cylinder portion (21c) surrounding the end plate portion (22g) of the piston (22),
An outermost fluid chamber (23d) is formed between the outer peripheral surface of the end plate portion (22g) of the piston (22) and the inner peripheral surface of the outermost cylinder portion (21c),
The blade (24) discharges the innermost fluid chamber (23a), the inner fluid chamber (23b), the outer fluid chamber (23c), and the outermost fluid chamber (23d) from the low pressure chamber on the suction side. A rotary compressor characterized in that it is partitioned into a high-pressure chamber on the side.

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