SCROLL COMPRESSOR

Abstract

A scroll compressor includes a housing having a fixed block, a driving shaft, a fixed scroll, and a movable scroll. The fixed block has a block side suction passage. Fluid is compressed in a compression chamber. The fixed scroll has a scroll side suction passage. The block side suction passage consists of first to third block side suction passages. The scroll side suction passage consists of first to third scroll side suction passages. The second and third scroll side suction passages are located away from a first specific region, and the third scroll side suction passage is located away from a second specific region.

Description

CROSS-REFERENCE TO RELATED APPLICATION

This application claims priority to Japanese Patent Application No. 2025-004575 filed on January 14, 2025, the entire disclosure of which is incorporated herein by reference.

BACKGROUND ART

The present disclosure relates to a scroll compressor.

A conventional scroll compressor is disclosed in Japanese Patent Application Publication Nos. H04-262085 (first Publication) and 2023-108766 (second Publication). The scroll compressor in the first Publication includes a housing, a driving shaft, a fixed scroll, and a movable scroll. A suction pipe is provided in the housing. Fluid is sucked from an outside of the housing into the housing through the suction pipe. An electric motor is also provided in the housing. Note that in the first Publication, specifically, the fluid is refrigerant gas.

The driving shaft is provided in the housing and is fixed to the electric motor. The driving shaft is rotatable around a driving axis in the housing with rotation of the electric motor. The fixed scroll is fixed inside the housing. The movable scroll is provided in the housing. The movable scroll is connected to the driving shaft.

In this scroll compressor, the housing has a fixed block. The fixed block is located between the electric motor and a set of the fixed scroll and the movable scroll in a direction in which the driving axis extends. The driving shaft is rotatably inserted through the fixed block. In addition, a pipe is press-fitted into the fixed block. The fluid can flow through the pipe.

In this scroll compressor, a first suction passage and a second suction passage are formed in the fixed scroll. The first suction passage directly communicates with the suction pipe. The second suction passage is disposed at a position shifted by 180 degrees from the first suction passage in a circumferential direction of the fixed scroll. That is, the first suction passage and the second suction passage are disposed opposite to each other across the driving axis in the circumferential direction of the fixed scroll. The first suction passage and the second suction passage communicate with each other through the pipe.

In this scroll compressor, the driving shaft is rotated by the electric motor, so that the movable scroll orbits relative to the fixed scroll. This forms a compression chamber between the fixed scroll and the movable scroll in which the fluid is compressed. In this scroll compressor, the fluid flows to the first suction passage of the fixed scroll through the suction pipe. A part of the fluid, which has flowed to the first suction passage, flows to the second suction passage through the pipe. Thus, the fluid is sucked into the compression chamber through each of the first suction passage and the second suction passage, and then, is compressed in the compression chamber.

The scroll compressor in the second Publication includes a housing, a driving shaft, an electric motor, a fixed scroll, and a movable scroll. A suction chamber into which fluid is sucked is formed in the housing. Note that in the second Publication, specifically, the fluid is refrigerant.

The housing includes a fixed block. The fixed block is located between the electric motor and a set of the fixed scroll and the movable scroll in the direction in which the driving axis extends. The driving shaft is rotatably supported by the housing therein. The driving shaft is rotatably inserted through the fixed block. The electric motor is provided in the suction chamber and rotates the driving shaft. The fixed scroll has a fixed scroll end plate, a fixed scroll spiral wall, and a fixed scroll peripheral wall. The fixed scroll spiral wall and the fixed scroll peripheral wall protrude from the fixed scroll end plate. The fixed scroll peripheral wall surrounds the fixed scroll spiral wall. The movable scroll is connected to the driving shaft. The movable scroll has a movable scroll spiral wall meshing with the fixed scroll spiral wall. The movable scroll and the fixed block are coupled to each other by an anti-rotation mechanism that prevents the movable scroll from rotating on its own axis.

In this scroll compressor, six block side suction passages are formed in the fixed block. The block side suction passages each communicate with the suction chamber, and the fluid in the suction chamber flows toward the fixed scroll through the block side suction passages. These block side suction passages are arranged at regular intervals in a rotational direction of the driving shaft. On the other hand, six scroll side suction passages are formed in the fixed scroll. Each of the scroll side suction passages communicates with a corresponding one of the block side suction passages. Similarly to the block side suction passages, the scroll side suction passages are arranged at regular intervals in the rotational direction of the driving shaft.

In this scroll compressor, the driving shaft is rotated by the electric motor, so that the movable scroll orbits relative to the fixed scroll. This forms a compression chamber between the fixed scroll spiral wall and the movable scroll spiral wall. The fluid in the suction chamber is sucked into the compression chamber through the six block side suction passages and the six scroll side suction passages, and is compressed in the compression chamber.

In this type of scroll compressor, higher compression efficiency in fluid and high quietness are required. In this regard, in the scroll compressor of the second Publication, the six block side suction passages are formed in the fixed block, and the six scroll side suction passages are formed in the fixed scroll. These block side suction passages and scroll side suction passages increase a flow rate of the fluid that is sucked from the suction chamber into the compression chamber.

However, in a case where a plurality of the block side suction passages and a plurality of the scroll side suction passages are formed as described above, there is a risk that once sucked fluid with the rotation of the movable scroll flows back to the block side suction passages, which causes a decrease of the compression efficiency.

Specifically, in the scroll compressor of the second Publication, a portion where a spiral end portion of the movable scroll spiral wall of the movable scroll and the fixed scroll peripheral wall of the fixed scroll are in contact with each other is defined as a closure portion. Of the six scroll side suction passages, one scroll side suction passage closest to the closure portion is defined as a first scroll side suction passage, another scroll side suction passage located on a leading side of the first scroll side suction passage in a rotational direction of the movable scroll is defined as a second scroll side suction passage, and another scroll side suction passage located on a trailing side of the first scroll side suction passage in the rotational direction of the movable scroll is defined as a third scroll side suction passage. Of the six block side suction passages, one block side suction passage that communicates with the first scroll side suction passage is defined as a first block side suction passage, another block side suction passage that communicates with the second scroll side suction passage is defined as a second block side suction passage, and another block side suction passage that communicates with the third scroll side suction passage is defined as a third block side suction passage.

In this case, most of the fluid is sucked from the suction chamber into the compression chamber through the second block side suction passage and the second scroll side suction passage. On the other hand, a part of the fluid sucked into the compression chamber is pushed toward the third scroll side suction passage when an outermost wall of the movable scroll spiral wall approaches the fixed scroll peripheral wall, so that the fluid may flow back from the third scroll side suction passage to the third block side suction passage. This may cause the decrease of the compression efficiency.

Thus, only by simply forming the plurality of the block side suction passages in the fixed block and forming the plurality of the scroll side suction passages in the fixed scroll, it is difficult to improve suction efficiency in the fluid that is sucked from the suction chamber toward the compression chamber, and hence, the compression efficiency in fluid.

The present disclosure is made in view of the above-described conventional circumstances, and is directed to providing a scroll compressor that is superior in compression efficiency in fluid and has high quietness.

SUMMARY

In accordance with an aspect of the present disclosure, there is provided a scroll compressor that includes a housing including a suction chamber into which fluid is sucked, a driving shaft provided in the housing, the driving shaft being rotatable around a driving axis, a fixed scroll fixed to the housing, and a movable scroll provided in the housing, the movable scroll being connected to the driving shaft. The housing has a fixed block that is located between the suction chamber and a set of the fixed scroll and the movable scroll, and through which the driving shaft is rotatably inserted. The movable scroll and the fixed block is coupled to each other by an anti-rotation mechanism that prevents the movable scroll from rotating on an axis of the movable scroll. The fluid is compressed in a compression chamber by the movable scroll orbiting relative to the fixed scroll, the compression chamber being formed between the fixed scroll and the movable scroll. The fixed block has a block side suction passage that communicates with the suction chamber and through which the fluid in the suction chamber flows toward the fixed scroll. The fixed scroll has a scroll side suction passage that is recessed in a direction in which the driving axis extends, that faces the block side suction passage in the direction in which the driving axis extends and communicates with the block side suction passage, and through which the fluid is sucked from the block side suction passage toward the compression chamber. The block side suction passage consists of a first block side suction passage, a second block side suction passage, and a third block side suction passage that are arranged away from each other in a rotational direction of the driving shaft. The scroll side suction passage consists of a first scroll side suction passage that communicates with the first block side suction passage, a second scroll side suction passage that is located away from the first scroll side suction passage in the rotational direction of the driving shaft and communicates with the second block side suction passage, and a third scroll side suction passage that is located away from the first scroll side suction passage and the second scroll side suction passage in the rotational direction of the driving shaft and communicates with the third block side suction passage. A portion of the fixed scroll opposite to the first scroll side suction passage across the driving axis is defined as a first specific region. A portion of the fixed scroll opposite to the second scroll side suction passage across the driving axis is defined as a second specific region. The second scroll side suction passage and the third scroll side suction passage are located away from the first specific region in a circumferential direction of the fixed scroll, and the third scroll side suction passage is located away from the second specific region in the circumferential direction of the fixed scroll.

Other aspects and advantages of the disclosure will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

The disclosure, together with objects and advantages thereof, may best be understood by reference to the following description of the embodiments together with the accompanying drawings in which:

FIG. 1 is a cross-sectional view of a scroll compressor according to a first embodiment;

FIG. 2 is a front view of a fixed block of the scroll compressor according to the first embodiment;

FIG. 3 is a front view of a fixed scroll of the scroll compressor according to the first embodiment;

FIG. 4 is a schematic view illustrating a positional relationship among first to third scroll side suction passages of the scroll compressor according to the first embodiment;

FIG. 5 is a graph showing magnitude of first-order suction pulsation in the scroll compressor according to the first embodiment;

FIG. 6 is a graph showing magnitude of second-order suction pulsation in the scroll compressor according to the first embodiment;

FIG. 7 is a front view of a fixed block of a scroll compressor according to a second embodiment;

FIG. 8 is a front view of a fixed scroll of the scroll compressor according to the second embodiment;

FIG. 9 is a schematic view illustrating a positional relationship among first to third scroll side suction passages of the scroll compressor according to the second embodiment;

FIG. 10 is a front view of a fixed scroll of a scroll compressor according to a first comparative example;

FIG. 11 is a graph showing magnitude of first-order suction pulsation in the scroll compressor according to the first comparative example;

FIG. 12 is a graph showing magnitude of second-order suction pulsation in the scroll compressor according to the first comparative example;

FIG. 13 is a front view of a fixed scroll of a scroll compressor according to a second comparative example;

FIG. 14 is a graph showing magnitude of first-order suction pulsation in the scroll compressor according to the second comparative example; and

FIG. 15 is a graph showing magnitude of second-order suction pulsation in the scroll compressor according to the second comparative example.

DETAILED DESCRIPTION OF THE EMBODIMENTS

The following will describe first and second embodiments according to the present disclosure with reference to the drawings. A scroll compressor (hereinafter, simply referred to as the compressor) of each of the first and second embodiments is, specifically, a scroll electric compressor. The compressor of each of the first and second embodiments is mounted on a vehicle, which is not illustrated, and serves as a part of a refrigerant circuit of the vehicle.

First embodiment

As illustrated in FIG. 1, the compressor of the first embodiment includes a housing 1, a driving shaft 5, an electric motor 7, a fixed scroll 9, and a movable scroll 11.

In the present embodiment, a front-rear direction and an up-down direction of the compressor are defined by solid arrows illustrated in FIG. 1. In FIG. 2 and the subsequent drawings, the up-down direction of the compressor is defined in correspondence with FIG. 1. Note that this front-rear direction and the up-down direction are examples for ease of explanation, and a posture of the compressor is changed as appropriate in correspondence with a vehicle on which the compressor is mounted, or the like.

As illustrated in FIG. 1, the housing 1 includes a motor housing 13, a compressor housing 14, and a fixed block 15. These motor housing 13, compressor housing 14, and fixed block 15 are each made of metal such as an aluminum alloy. The motor housing 13 corresponds to a front portion of the housing 1, and the compressor housing 14 corresponds to a rear portion of the housing 1.

The motor housing 13 has a front wall 13a and a first peripheral wall 13b. The front wall 13a is located at a front end of the motor housing 13 and extends in a radial direction of the motor housing 13. The first peripheral wall 13b is connected to the front wall 13a and is formed in a substantially cylindrical shape extending rearward from the front wall 13a. These front wall 13a and first peripheral wall 13b form the motor housing 13 having a bottomed tubular shape with its rear end open. A suction chamber 17 is formed in the motor housing 13.

First bolt holes 51 are formed in the first peripheral wall 13b. The first bolt holes 51 are recessed and extend forward from a rear end surface of the first peripheral wall 13b. Although not illustrated, six first bolt holes 51 are formed in the first peripheral wall 13b and are arranged at regular intervals in a circumferential direction of the first peripheral wall 13b. In FIG. 1, one of the six first bolt holes 51 is illustrated.

The motor housing 13 also has a suction opening 13c and a supporting portion 13d. The suction opening 13c is formed in the first peripheral wall 13b, opens toward an upper side of the first peripheral wall 13b, and communicates with the suction chamber 17. The suction opening 13c is connected to an evaporator through a pipe, and refrigerant gas flowing through the evaporator is sucked into the suction chamber 17 through the suction opening 13c. Here, illustrations of the evaporator and the pipe are omitted. The refrigerant gas is an example of the “fluid” in the present disclosure.

The supporting portion 13d protrudes from the front wall 13a into the suction chamber 17. The supporting portion 13d is formed in a cylindrical shape and has a first radial bearing 19 therein. Note that the suction opening 13c may be formed in the front wall 13a.

The compressor housing 14 has a rear wall 14a and a second peripheral wall 14b. The rear wall 14a is located at a rear end of the compressor housing 14 and extends in a radial direction of the compressor housing 14. The second peripheral wall 14b is connected to the rear wall 14a and is formed in a substantially cylindrical shape extending forward from the rear wall 14a. These rear wall 14a and second peripheral wall 14b form the compressor housing 14 having a bottomed tubular shape with its front end open.

Second bolt holes 52 are formed in the second peripheral wall 14b. The second bolt holes 52 extend through the second peripheral wall 14b in a direction in which a driving axis O extends. The driving axis O is parallel to the front-rear direction. Although not illustrated, six second bolt holes 52 are formed in the second peripheral wall 14b and are arranged at regular intervals in a circumferential direction of the second peripheral wall 14b. In FIG. 1, one of the six second bolt holes 52 is illustrated.

An oil separation chamber 14c, a discharge recess 14d, a discharge passage 14e, and a discharge opening 14f are formed in the compressor housing 14. The oil separation chamber 14c is formed inside the rear wall 14a and extends in the radial direction of the compressor housing 14. The discharge recess 14d is formed in the rear wall 14a. The discharge recess 14d is recessed toward the oil separation chamber 14c, that is, rearward. The discharge passage 14e is formed inside the rear wall 14a and extends from the oil separation chamber 14c to the discharge recess 14d in the direction in which the driving axis O extends. Thus, the oil separation chamber 14c and the discharge recess 14d communicate with each other through the discharge passage 14e. The discharge opening 14f is formed in the rear wall 14a. The discharge opening 14f communicates with an upper end of the oil separation chamber 14c and opens toward an upper side of the rear wall 14a. The discharge opening 14f is connected to a condenser through a pipe. Here, illustrations of the condenser and the pipe are omitted.

A separation cylinder 21 is fixed in the oil separation chamber 14c. A separator is formed of an inner peripheral surface of the oil separation chamber 14c and an outer peripheral surface of the separation cylinder 21. In the oil separation chamber 14c, a filter 23 is provided under the separation cylinder 21.

The fixed block 15 is provided between the motor housing 13 and the compressor housing 14. The fixed block 15 is located between the suction chamber 17 and a set of the fixed scroll 9 and the movable scroll 11 in the direction in which the driving axis O extends. The fixed block 15 has a block main body 15a and a boss 15b.

The block main body 15a is formed in a disc shape having substantially the same diameter as those of the first peripheral wall 13b of the motor housing 13 and the second peripheral wall 14b of the compressor housing 14. The block main body 15a has a front end surface 151 that is oriented forward and a rear end surface 152 that is located opposite to the front end surface 151 and oriented rearward. A recess 153 is formed at a center of the block main body 15a. The recess 153 is recessed in a columnar shape extending forward from the rear end surface 152 around the driving axis O.

As illustrated in FIG. 2, six third bolt holes 53 are formed in the block main body 15a. The third bolt holes 53 extend through the block main body 15a in the direction in which the driving axis O extends. The third bolt holes 53 are arranged at regular intervals in a circumferential direction of the block main body 15a. Note that one of the six third bolt holes 53 is illustrated in FIG. 1.

A block side suction passage 61 is formed in the block main body 15a. As illustrated in FIG. 2, the block side suction passage 61 consists of a first block side suction passage 61a, a second block side suction passage 61b, and a third block side suction passage 61c.

The first to third block side suction passages 61a to 61c are disposed inside the third bolt holes 53 in a radial direction of the fixed block 15 in the block main body 15a. The first to third block side suction passages 61a to 61c are each disposed between adjacent two of the third bolt holes 53.

The first block side suction passage 61a is formed so as to correspond to a first scroll side suction passage 71a, which will be described later. The second block side suction passage 61b is formed so as to correspond to a second scroll side suction passage 71b, which will be described later. The third block side suction passage 61c is formed so as to correspond to a third scroll side suction passage 71c, which will be described later.

The first to third block side suction passages 61a to 61c are each formed in an elongated hole shape extending in the circumferential direction of the block main body 15a. Here, shapes of the first to third block side suction passages 61a to 61c also correspond to shapes of the first to third scroll side suction passages 71a to 71c, respectively. The first to third block side suction passages 61a to 61c are arranged with respective predetermined distances from each other in the circumferential direction of the block main body 15a. The arrangement of the first to third block side suction passages 61a to 61c in the block main body 15a will be described later in detail. Note that the shapes and sizes of the first to third block side suction passages 61a to 61c may be designed as appropriate, and for example, the first to third block side suction passages 61a to 61c may be formed in the same shape or in different shapes.

As illustrated in FIG. 1, four orbiting pins 31 are fixed to the block main body 15a. The orbiting pins 31 extend out of the rear end surface 152 of the block main body 15a. Although detailed illustrations are omitted, the orbiting pins 31 are arranged at regular intervals in the circumferential direction of the block main body 15a. Note that one of the four orbiting pins 31 is illustrated in FIG. 1.

The boss 15b is formed integrally with the block main body 15a and is located inside the first to third block side suction passages 61a to 61c in the radial direction of the block main body 15a. The boss 15b is formed in a bottomed cylindrical shape protruding forward from the front end surface 151 of the block main body 15a. An insertion hole 15c is formed at a distal end of the boss 15b. The insertion hole 15c communicates with an inside of the boss 15b. The inside of the boss 15b communicates with the recess 153. A second radial bearing 27 and a sealing member 29 are provided inside the boss 15b.

The driving shaft 5 is provided in the housing 1. The driving shaft 5 is formed in a columnar shape extending in the direction in which the driving axis O extends. The driving shaft 5 has a small diameter portion 5a, a large diameter portion 5b, and a taper portion 5c. The small diameter portion 5a is located on a front end side of the driving shaft 5. The large diameter portion 5b is located behind the small diameter portion 5a. The large diameter portion 5b is formed to be larger than the small diameter portion 5a. The taper portion 5c is located between the small diameter portion 5a and the large diameter portion 5b. The taper portion 5c is connected to the small diameter portion 5a at a front end of the taper portion 5c. The taper portion 5c increases in diameter as the taper portion 5c extends rearward, and is connected to the large diameter portion 5b at a rear end of the taper portion 5c.

The small diameter portion 5a of the driving shaft 5 is rotatably supported by the supporting portion 13d of the motor housing 13 through the first radial bearing 19. A rear end portion of the large diameter portion 5b is inserted through the insertion hole 15c of the fixed block 15 and enters the inside of the boss 15b. The rear end portion of the large diameter portion 5b is rotatably supported through the second radial bearing 27 inside the boss 15b. The sealing member 29 provides a seal between the insertion hole 15c and the driving shaft 5. Thus, the driving shaft 5 is rotatably inserted through the fixed block 15 and is rotatable around the driving shaft 5 inside the housing 1. More specifically, in this compressor, the driving shaft 5 is rotatable around the driving axis O in a rotational direction R1 illustrated in FIGS. 2 to 4.

As illustrated in FIG. 1, an eccentric pin 50 is fixed to a rear end of the large diameter portion 5b of the driving shaft 5. The eccentric pin 50 is disposed at a position eccentric to the driving axis O in the large diameter portion 5b, and by extension, in the driving shaft 5. The eccentric pin 50 is formed in a columnar shape with a diameter smaller than that of the driving shaft 5, and extends rearward from the rear end of the large diameter portion 5b. When the rear end portion of the large diameter portion 5b is inserted into the insertion hole 15c, the eccentric pin 50 enters the recess 153. The eccentric pin 50 is fitted into a bushing 6 inside the recess 153.

A balance weight 6a is formed integrally with the bushing 6. The balance weight 6a extends outward in a radial direction of the driving shaft 5 from the bushing 6 inside the recess 153. That is, the balance weight 6a extends in the radial direction of the driving shaft 5 so as to be eccentric to the driving axis O. Thus, when the eccentric pin 50 is fitted into the bushing 6, the balance weight 6a is disposed at a position on a side opposite from the eccentric pin 50 across the driving axis O. Then, the balance weight 6a rotates together with the bushing 6 inside the recess 153 with the rotation of the driving shaft 5. Note that a shape of the balance weight 6a may be designed as appropriate.

The electric motor 7 is accommodated inside the housing 1, more specifically, inside the suction chamber 17. That is, the suction chamber 17 also serves as a motor chamber in which the electric motor 7 is accommodated. The electric motor 7 is located in front of the fixed block 15.

The electric motor 7 includes a stator 7a and a rotor 7b. The stator 7a is connected to an inverter, which is not illustrated, provided outside the motor housing 13.

The stator 7a has a stator core 701 and coil ends 703. The stator core 701 is formed in a cylindrical shape and is fixed to an inner peripheral surface of the first peripheral wall 13b. A lead wire 705 is wound around the stator core 701. The coil ends 703 are each formed in a ring shape and protrude forward and rearward from the stator core 701 in the direction in which the driving axis O extends. A part of the lead wire 705 forms the coil ends 703.

The rotor 7b is formed in a cylindrical shape extending in the direction in which the driving axis O extends and is disposed in the stator 7a. The large diameter portion 5b of the driving shaft 5 is press-fitted into the rotor 7b. As a result, the driving shaft 5 is fixed to the rotor 7b. The rotor 7b rotates inside the stator 7a, thereby rotating the driving shaft 5 around the driving axis O.

The fixed scroll 9 is made of metal such as an aluminum alloy. The fixed scroll 9 has a fixed scroll end plate 9a, a fixed scroll peripheral wall 9b, and a fixed scroll spiral wall 9c. The fixed scroll end plate 9a is located at a rear end of the fixed scroll 9 and is formed in a disc shape. A discharge port 9d is formed in the fixed scroll end plate 9a. The discharge port 9d extends through the fixed scroll end plate 9a in the direction in which the driving axis O extends. A discharge reed valve 38 and a retainer 39 are attached to the fixed scroll end plate 9a with a fixing bolt 37. The discharge reed valve 38 is elastically deformed to open and close the discharge port 9d. The retainer 39 adjusts an amount of the elastic deformation of the discharge reed valve 38.

The fixed scroll peripheral wall 9b is formed in a cylindrical shape extending in the direction in which the driving axis O extends. The fixed scroll peripheral wall 9b has a peripheral wall main body portion 91 and a flange portion 92. The peripheral wall main body portion 91 is connected to the fixed scroll end plate 9a at an outer periphery of the fixed scroll end plate 9a and extends forward from the fixed scroll end plate 9a. The flange portion 92 is connected to a front end of the peripheral wall main body portion 91. That is, the flange portion 92 is located at a front end of the fixed scroll peripheral wall 9b, and by extension, at a front end of the fixed scroll 9. Accordingly, in the fixed scroll peripheral wall 9b, the peripheral wall main body portion 91 is located outside the fixed scroll spiral wall 9c in a radial direction of the fixed scroll 9, and the flange portion 92 is located in front of the fixed scroll spiral wall 9c. A diameter of the flange portion 92 is larger than that of the peripheral wall main body portion 91.

The fixed scroll spiral wall 9c is formed integrally with the fixed scroll end plate 9a and extends forward in the direction in which the driving axis O extends from a front end surface of the fixed scroll end plate 9a. In addition, as illustrated in FIG. 3, when an end of the fixed scroll spiral wall 9c on a central side of the fixed scroll end plate 9a is defined as a leading end 901 of its spiral, the fixed scroll spiral wall 9c has a spiral shape extending outward in the radial direction of the fixed scroll 9 from the leading end 901. The fixed scroll spiral wall 9c is formed integrally with the peripheral wall main body portion 91 on an inner side thereof.

Although a detailed illustration is omitted, an oil supply passage is formed in the fixed scroll 9. The oil supply passage extends through the fixed scroll end plate 9a and the fixed scroll peripheral wall 9b. Thus, the oil supply passage opens in a rear end surface of the fixed scroll end plate 9a at a rear end of the oil supply passage, and opens in the flange portion 92 at a front end of the oil supply passage. The oil supply passage communicates with the oil separation chamber 14c through the filter 23. Note that a shape of the oil supply passage may be designed as appropriate.

As illustrated in FIG. 3, six fourth bolt holes 54 are formed in the fixed scroll 9. The fourth bolt holes 54 are formed in the flange portion 92 and extend through the flange portion 92 in the direction in which the driving axis O extends. The fourth bolt holes 54 are arranged at regular intervals in a circumferential direction of the flange portion 92, and by extension, the fixed scroll 9. Note that one of the six fourth bolt holes 54 is illustrated in FIG. 1.

A scroll side suction passage 71 is recessed in the fixed scroll peripheral wall 9b of the fixed scroll 9 in the direction in which the driving axis O extends. As illustrated in FIG. 3, the scroll side suction passage 71 consists of the first scroll side suction passage 71a, the second scroll side suction passage 71b, and the third scroll side suction passage 71c. In the fixed scroll 9, the first to third scroll side suction passages 71a to 71c, that is, the scroll side suction passage 71 is located outside the fixed scroll spiral wall 9c in the radial direction of the fixed scroll 9 and inside the fourth bolt holes 54 in the radial direction of the fixed scroll 9.

The first to third scroll side suction passages 71a to 71c open in the flange portion 92 and extend rearward, that is, from the flange portion 92 toward the peripheral wall main body portion 91 in the direction in which the driving axis O extends. The first to third scroll side suction passages 71a to 71c are each formed in a substantially rectangular elongated hole shape extending in the circumferential direction of the fixed scroll 9.

The second scroll side suction passage 71b is shorter in the circumferential direction of the fixed scroll 9 than the first scroll side suction passage 71a and the third scroll side suction passage 71c. Note that as long as the first to third scroll side suction passages 71a to 71c extend rearward in the direction in which the driving axis O extends, their shapes and sizes may be designed as appropriate. For example, the first to third scroll side suction passages 71a to 71c may be formed in the same shape or in different shapes.

These first to third scroll side suction passages 71a to 71c are arranged with respective predetermined distances from each other in the circumferential direction of the fixed scroll 9. More specifically, in the rotational direction R1 of the driving shaft 5, the first scroll side suction passage 71a, the second scroll side suction passage 71b, and the third scroll side suction passage 71c are arranged in this order. In addition, the scroll side suction passages 71a to 71c are each disposed between adjacent two of the fourth bolt holes 54.

Here, a portion of the fixed scroll peripheral wall 9b of the fixed scroll 9 opposite to the first scroll side suction passage 71a across the driving axis O is defined as a first specific region X1. A portion of the fixed scroll peripheral wall 9b opposite to the second scroll side suction passage 71b across the driving axis O is defined as a second specific region X2. A portion of the fixed scroll peripheral wall 9b opposite to the third scroll side suction passage 71c across the driving axis O is defined as a third specific region X3.

In this fixed scroll 9, the second scroll side suction passage 71b and the third scroll side suction passage 71c are each located away from the first specific region X1 in the circumferential direction of the fixed scroll 9. The third scroll side suction passage 71c and the first scroll side suction passage 71a are each located away from the second specific region X2 in the circumferential direction of the fixed scroll 9. The first scroll side suction passage 71a and the second scroll side suction passage 71b are each located away from the third specific region X3 in the circumferential direction of the fixed scroll 9.

In other words, in the circumferential direction of the fixed scroll 9, the first specific region X1 is located between the second scroll side suction passage 71b and the third scroll side suction passage 71c. In the circumferential direction of the fixed scroll 9, the second specific region X2 is located between the third scroll side suction passage 71c and the first scroll side suction passage 71a. In the circumferential direction of the fixed scroll 9, the third specific region X3 is located between the first scroll side suction passage 71a and the second scroll side suction passage 71b.

As a result, in this fixed scroll 9, neither the second scroll side suction passage 71b nor the third scroll side suction passage 71c is disposed opposite to the first scroll side suction passage 71a at 180 degrees in the circumferential direction of the fixed scroll 9. Neither the third scroll side suction passage 71c nor the first scroll side suction passage 71a is disposed opposite to the second scroll side suction passage 71b at 180 degrees in the circumferential direction of the fixed scroll 9. Neither the first scroll side suction passage 71a nor the second scroll side suction passage 71b is disposed opposite to the third scroll side suction passage 71c at 180 degrees in the circumferential direction of the fixed scroll 9. That is, in the fixed scroll 9, the first to third scroll side suction passages 71a to 71c are not disposed opposite to each other at 180 degrees in the circumferential direction of the fixed scroll 9.

As illustrated in FIG. 4, in the fixed scroll 9, a first imaginary line L1 extending straight through a center of the first scroll side suction passage 71a and the driving axis O, a second imaginary line L2 extending straight through a center of the second scroll side suction passage 71b and the driving axis O, and a third imaginary line L3 extending straight through a center of the third scroll side suction passage 71c and the driving axis O are defined.

An angle between the first imaginary line L1 and the second imaginary line L2 in the rotational direction R1 of the driving shaft 5 is defined as a first angle θ1. An angle between the second imaginary line L2 and the third imaginary line L3 in the rotational direction R1 of the driving shaft 5 is defined as a second angle θ2. An angle between the first imaginary line L1 and the third imaginary line L3 in a direction opposite to the rotational direction R1 of the driving shaft 5 is defined as a third angle θ3.

That is, the first angle θ1 corresponds to a distance between the first scroll side suction passage 71a and the second scroll side suction passage 71b in the rotational direction R1 of the driving shaft 5. Similarly, the second angle θ2 corresponds to a distance between the second scroll side suction passage 71b and the third scroll side suction passage 71c in the rotational direction R1 of the driving shaft 5. The third angle θ3 corresponds to a distance between the first scroll side suction passage 71a and the third scroll side suction passage 71c in the direction opposite to the rotational direction R1 of the driving shaft 5. Note that in FIG. 4, portions of the fixed scroll 9 are illustrated by broken lines. The same goes for FIG. 9, which will be described later.

Here, these first angle θ1, second angle θ2, and third angle θ3 are each different from 120 degrees. In detail, the first angle θ1 and the third angle θ3 are each greater than 120 degrees, and the second angle θ2 is smaller than 120 degrees. As a result, in the fixed scroll peripheral wall 9b, these first to third scroll side suction passages 71a to 71c are not arranged at regular intervals in the circumferential direction of the fixed scroll 9.

As described above, the first to third block side suction passages 61a to 61c illustrated in FIG. 2 are formed so as to correspond to the first to third scroll side suction passages 71a to 71c, respectively. Thus, in the rotational direction R1 of the driving shaft 5, the first block side suction passage 61a, the second block side suction passage 61b, and the third block side suction passage 61c are arranged in this order in the block main body 15a of the fixed block 15. The second block side suction passage 61b has an elongated hole shape and is shorter than each of the first block side suction passage 61a and third block side suction passage 61c in the circumferential direction of the fixed block 15. In the block main body 15a, the first to third block side suction passages 61a to 61c are not located opposite to each other at 180 degrees in the circumferential direction of the fixed block 15. In addition, the first to third block side suction passages 61a to 61c are not arranged at regular intervals in the circumferential direction of the fixed block 15.

As illustrated in FIG. 1, the movable scroll 11 is provided in the compressor housing 14 and is located between the fixed scroll 9 and the fixed block 15. The movable scroll 11 has a movable scroll end plate 11a and a movable scroll spiral wall 11b. The movable scroll 11 is made of metal such as an aluminum alloy.

The movable scroll end plate 11a is located at a front end of the movable scroll 11 and has a disc shape. The bushing 6 is rotatably supported by the movable scroll end plate 11a through a third radial bearing 45. Thus, the movable scroll 11 is connected to the driving shaft 5 at a position eccentric to the driving axis O through the bushing 6 and the eccentric pin 50.

Four rings 47 are fixed to the movable scroll end plate 11a. Although not illustrated in detail, the rings 47 are arranged at regular intervals in a circumferential direction of the movable scroll end plate 11a so as to correspond to the orbiting pins 31. Note that one of the four rings 47 is illustrated in FIG. 1.

The movable scroll spiral wall 11b protrudes from a rear end surface of the movable scroll end plate 11a and extends toward the fixed scroll end plate 9a in the direction in which the driving axis O extends. When an end of the movable scroll spiral wall 11b on a central side of the movable scroll end plate 11a is defined as a leading end 110 of its spiral, the movable scroll spiral wall 11b has a spiral shape extending outward in a radial direction of the movable scroll end plate 11a from the leading end 110.

An air supply passage, which is not illustrated, is formed in the movable scroll 11. The air supply passage extends through the movable scroll 11 in the direction in which the driving axis O extends. Thus, the air supply passage, at a rear end thereof, opens in a rear end of the movable scroll spiral wall 11b near the center thereof. The air supply passage extends straight forward through the movable scroll spiral wall 11b and opens in a front end surface of the movable scroll end plate 11a.

As illustrated in FIG. 1, the movable scroll 11 enters an inside of the fixed scroll peripheral wall 9b with the movable scroll spiral wall 11b facing the fixed scroll end plate 9a of the fixed scroll 9. This causes the fixed scroll spiral wall 9c and the movable scroll spiral wall 11b to mesh with each other inside the fixed scroll peripheral wall 9b, more specifically, inside the peripheral wall main body portion 91. As a result, a compression chamber 49 is formed of the fixed scroll end plate 9a, the fixed scroll spiral wall 9c, the movable scroll end plate 11a, and the movable scroll spiral wall 11b inside the peripheral wall main body portion 91. Note that, technically speaking, a closed space defined by the fixed scroll end plate 9a, the fixed scroll spiral wall 9c, the movable scroll end plate 11a, and the movable scroll spiral wall 11b inside the peripheral wall main body portion 91 with rotation of the movable scroll 11 is the compression chamber 49. The compression chamber 49 changes its volume with the rotation of the movable scroll 11. The compression chamber 49 communicates with the discharge port 9d with the rotation of the movable scroll 11.

The fixed block 15 is disposed in front of the fixed scroll 9 and the movable scroll 11. Thus, the orbiting pins 31 enter the corresponding rings 47. An anti-rotation mechanism 16 is formed by coupling the orbiting pins 31 to the corresponding rings 47. In the anti-rotation mechanism 16, each of the orbiting pins 31 rolls while sliding on an inner peripheral surface of the corresponding one of the rings 47, thereby preventing the rotation of the movable scroll 11 on its own axis relative to the fixed scroll 9 and only allowing the movable scroll 11 to orbit relative to the fixed scroll 9. The compression chamber 49 is formed between the fixed scroll 9 and the movable scroll 11, and the fluid is compressed in the compression chamber 49 by the movable scroll 11 orbiting relative to the fixed scroll 9. Note that the number of the orbiting pins 31 and the rings 47 that form the anti-rotation mechanism 16 may be determined as appropriate, as long as the number is three or more. In addition, the anti-rotation mechanism 16 may be configured differently from the orbiting pins 31 and the rings 47.

A thrust plate 18 is provided between the movable scroll end plate 11a and the fixed block 15. The thrust plate 18 is made of a thin metal plate. The thrust plate 18 is capable of urging the movable scroll 11 rearward, that is, toward the fixed scroll 9, by a restoring force during elastic deformation of the thrust plate 18. The thrust plate 18 has six fifth bolt holes 55 and three communication holes 180. Note that one of the six fifth bolt holes 55 and one of the three communication holes 180 are illustrated in FIG. 1.

In this compressor, in a state where the movable scroll 11 enters the inside of the fixed scroll peripheral wall 9b as described above, the flange portion 92 of the fixed scroll peripheral wall 9b faces the block main body 15a of the fixed block 15 in the front-rear direction through the thrust plate 18. Then, the third bolt holes 53, the fourth bolt holes 54, and the fifth bolt holes 55 are aligned with each other in the front-rear direction.

In this compressor, the three communication holes 180, the block side suction passage 61 and the scroll side suction passage 71 are aligned with each other in the front-rear direction. Specifically, one of the three communication holes 180, the first block side suction passage 61a, and the first scroll side suction passage 71a are aligned with each other in the front-rear direction. Another of the three communication holes 180, the second block side suction passage 61b, and the second scroll side suction passage 71b are aligned with each other in the front-rear direction. Then, the remaining one of the three communication holes 180, the third block side suction passage 61c, and the third scroll side suction passage 71c are aligned with each other in the front-rear direction. Thus, in this compressor, the block side suction passage 61 and the scroll side suction passage 71 face each other in the direction in which the driving axis O extends and communicate with each other through the three communication holes 180.

In this compressor, in a state where the third bolt holes 53 are aligned with the first bolt holes 51 in the front-rear direction, the front end surface 151 of the block main body 15a is in contact with the first peripheral wall 13b of the motor housing 13 in the front-rear direction.

In this compressor, a gasket plate 24 is provided between the second peripheral wall 14b of the compressor housing 14 and the flange portion 92 of the fixed scroll peripheral wall 9b. The gasket plate 24 has six sixth bolt holes 56. In a state where the peripheral wall main body portion 91 of the fixed scroll peripheral wall 9b enters an inside of the second peripheral wall 14b, the second bolt holes 52, the sixth bolt holes 56, and the fourth bolt holes 54 are aligned with each other in the front-rear direction. Note that one of the six sixth bolt holes 56 is illustrated in FIG. 1.

Then, in this compressor, the motor housing 13, the fixed block 15, the thrust plate 18, the fixed scroll 9, the gasket plate 24, and the compressor housing 14 are fastened and fixed to each other in the direction in which the driving axis O extends, with six bolts 25 inserted from a side of the compressor housing 14 through the first to sixth bolt holes 51 to 56. That is, in this compressor, the fixed block 15, the thrust plate 18, the fixed scroll 9, and the gasket plate 24 are held by and fixed to the motor housing 13 and the compressor housing 14. Note that one of the six bolts 25 is illustrated in FIG. 1. In addition, a method of fixing the motor housing 13, the fixed block 15, the thrust plate 18, the fixed scroll 9, the gasket plate 24, and the compressor housing 14 may be designed as appropriate, not only with the bolts 25.

In this compressor, the fixed block 15 is located between the suction chamber 17 and the movable scroll 11 in the direction in which the driving axis O extends. Accordingly, the first to third block side suction passages 61a to 61c, that is, the block side suction passage 61 opens to and communicates with the suction chamber 17. In the fixed scroll peripheral wall 9b of the fixed scroll 9, whereas the peripheral wall main body portion 91 is located inside the compressor housing 14, the flange portion 92 is located outside the compressor housing 14. The gasket plate 24 provides a seal between the flange portion 92 and the second peripheral wall 14b of the compressor housing 14.

When the motor housing 13, and the like, are fixed with the bolts 25, a back pressure chamber 65 is defined by the recess 153 of the fixed block 15, the movable scroll 11, and the thrust plate 18. That is, the back pressure chamber 65 is formed in a substantially annular shape outside the driving shaft 5 and is located in front of the movable scroll end plate 11a of the movable scroll 11 with the thrust plate 18 interposed between the movable scroll end plate 11a and the back pressure chamber 65. The back pressure chamber 65 communicates with the air supply passage.

In this compressor, the peripheral wall main body portion 91 is located inside the compressor housing 14, so that the fixed scroll end plate 9a is in contact with the rear wall 14a inside the compressor housing 14. Thus, a discharge chamber 35 is defined by the discharge recess 14d and the fixed scroll end plate 9a. The discharge chamber 35 communicates with the discharge port 9d and the discharge passage 14e. In other words, the discharge chamber 35 communicates with the compression chamber 49 through the discharge port 9d.

In this compressor having the configuration as described above, the electric motor 7 is operated while being controlled by the inverter to rotate the driving shaft 5 around the driving axis O in the rotational direction R1. This rotates the movable scroll 11 in the rotational direction R1 in the state where the movable scroll 11 is eccentric to the driving axis O. Then, the movable scroll end plate 11a slides on a distal end of the fixed scroll spiral wall 9c, and the fixed scroll spiral wall 9c and the movable scroll spiral wall 11b slide on each other inside the fixed scroll peripheral wall 9b. Here, the movable scroll 11 is prevented from rotating on its own axis by the anti-rotation mechanism 16 and only orbits.

Thus, the refrigerant gas in the suction chamber 17 is sucked toward the compression chamber 49 through the block side suction passage 61, the communication holes 180, and the scroll side suction passage 71 with the rotation of the movable scroll 11.

Specifically, the refrigerant gas that has reached the first block side suction passage 61a flows from the first block side suction passage 61a to the first scroll side suction passage 71a through one of the communication holes 180. Then, this refrigerant gas flows from the first scroll side suction passage 71a to an inside of the peripheral wall main body portion 91, and then, is sucked toward the compression chamber 49 (see broken arrows in FIG. 1). Similarly, the refrigerant gas that has reached the second block side suction passage 61b flows to the second scroll side suction passage 71b through another of the communication holes 180, flows from the second scroll side suction passage 71b to the inside of the peripheral wall main body portion 91, and then, is sucked toward the compression chamber 49. Similarly, the refrigerant gas that has reached the third block side suction passage 61c flows to the third scroll side suction passage 71c through the remaining one of the communication holes 180, flows from the third scroll side suction passage 71c to the inside of the peripheral wall main body portion 91, and then, is sucked toward the compression chamber 49.

After that, the compression chamber 49 decreases its volume with the rotation of the movable scroll 11 to compress the refrigerant gas therein. The refrigerant gas at high pressure compressed in the compression chamber 49 is discharged to the discharge chamber 35 through the discharge port 9d, and flows from the discharge chamber 35 to the oil separation chamber 14c through the discharge passage 14e. Lubricating oil is separated from this refrigerant gas at high pressure while the refrigerant gas repeatedly circulates between the outer peripheral surface of the separation cylinder 21 and the inner peripheral surface of the oil separation chamber 14c. Then, the refrigerant gas flows through the separation cylinder 21 and is discharged to an outside of the housing 1 through the discharge opening 14f.

On the other hand, the lubricating oil separated from the refrigerant gas is stored in the oil separation chamber 14c. Then, this lubricating oil flows through the filter 23 and the oil supply passage, and is supplied to a sliding portion between the fixed scroll 9 and the movable scroll 11 to lubricate the sliding portion. The lubricating oil flowing through the oil supply passage is also supplied to the suction chamber 17, and the like, in addition to a space between the second radial bearing 27 and the driving shaft 5.

A part of the refrigerant gas at the high pressure compressed in the compression chamber 49 flows through the air supply passage and is supplied to the back pressure chamber 65. This increases pressure in the back pressure chamber 65. As a result, the movable scroll 11 is urged toward the compression chamber 49 by the pressure in the back pressure chamber 65 through the thrust plate 18. The movable scroll 11 is also urged toward the compression chamber 49 by an elastic force of the thrust plate 18. Thus, in this compressor, it is suppressed that the movable scroll 11 rotates in a state where the movable scroll 11 is inclined relative to the driving axis O.

Here, in this compressor, the block side suction passage 61 consists of the first to third block side suction passages 61a to 61c, and the scroll side suction passage 71 consists of the first to third scroll side suction passages 71a to 71c. With this configuration, in this compressor, a flow rate of the refrigerant gas that is sucked from the suction chamber 17 into the compression chamber 49 is sufficiently secured and suction pulsation during the operation of the compressor is suitably suppressed. The following will describe the operation of the compressor in detail in comparison with compressors of first and second comparative examples.

First comparative example

As illustrated in FIG. 10, the compressor of the first comparative example includes a fixed scroll 90. A scroll side suction passage 95 is recessed in this fixed scroll 90. The scroll side suction passage 95 consists of a first scroll side suction passage 95a and a second scroll side suction passage 95b. The first scroll side suction passage 95a and the second scroll side suction passage 95b are disposed opposite to each other at 180 degrees across the driving axis O.

Although not illustrated, in the compressor of the first comparative example, a first block side suction passage communicating with the first scroll side suction passage 95a and a second block side suction passage communicating with the second scroll side suction passage 95b are formed in the fixed block 15. Accordingly, in the compressor of the first comparative example, the first block side suction passage and the second block side suction passage are disposed opposite to each other at 180 degrees across the driving axis O. Other components of the compressor of the first comparative example, including other components of the fixed scroll 90 and the fixed block 15, are the same as those of the compressor of the first embodiment. The identical components are denoted by the identical reference numerals, and detailed descriptions of the components will be omitted.

In the compressor of the first comparative example, the refrigerant gas in the suction chamber 17 flows to the inside of the peripheral wall main body portion 91 through the first block side suction passage and the first scroll side suction passage 95a and through the second block side suction passage and the second scroll side suction passage 95b, and then, is sucked toward the compression chamber 49.

However, in the compressor of the first comparative example, the scroll side suction passage 95 consists of only two passages: the first scroll side suction passage 95a and second scroll side suction passage 95b, and the block side suction passage consists of only two passages: the first block side suction passage and the second block side suction passage. Accordingly, in the compressor of the first comparative example, it is difficult to sufficiently secure a flow rate of the refrigerant gas that is sucked from the suction chamber 17 toward the compression chamber 49, which makes it difficult to increase suction efficiency in the refrigerant gas. As a result, in the compressor of the first comparative example, it is difficult to increase compression efficiency in the refrigerant gas during the operation of the compressor.

Here, in the compressor of the first comparative example, the first scroll side suction passage 95a and the second scroll side suction passage 95b are disposed opposite to each other at 180 degrees across the driving axis O. Accordingly, as indicated by black arrows in a graph of FIG. 11, an orientation of a vector of first-order suction pulsation in the first scroll side suction passage 95a during the operation of the compressor is different from an orientation of a vector of first-order suction pulsation in the second scroll side suction passage 95b during the operation of the compressor. The first-order suction pulsation in the first scroll side suction passage 95a and the first-order suction pulsation in the second scroll side suction passage 95b are operated so that they cancel out each other. As a result, in the compressor of the first comparative example, as indicated by a white arrow in FIG. 11, a vector of first-order suction pulsation F30 as a whole during the operation of the compressor has small magnitude. That is, in the compressor of the first comparative example, the first-order suction pulsation F30 as a whole during the operation of the compressor may be reduced.

However, as indicated by black arrows in a graph of FIG. 12, in the compressor of the first comparative example, an orientation of a vector of second-order suction pulsation in the first scroll side suction passage 95a during the operation of the compressor is the same as that of a vector of second-order suction pulsation in the second scroll side suction passage 95b during the operation of the compressor. Thus, in the compressor of the first comparative example, a vector of second-order suction pulsation F40 as a whole during the operation of the compressor has large magnitude. That is, in the compressor of the first comparative example, the second-order suction pulsation F40 as a whole during the operation of the compressor has large magnitude, so that noise during the operation is increased.

Second comparative example

As illustrated in FIG. 13, the compressor of the second comparative example includes a fixed scroll 94. A scroll side suction passage 96 is recessed in this fixed scroll 94. The scroll side suction passage 96 consists of a first scroll side suction passage 96a, a second scroll side suction passage 96b, a third scroll side suction passage 96c, a fourth scroll side suction passage 96d, a fifth scroll side suction passage 96e, and a sixth scroll side suction passage 96f. These first to sixth scroll side suction passages 96a to 96f are arranged at regular intervals in a circumferential direction of the fixed scroll 94.

Although not illustrated, in the compressor of the second comparative example, first to sixth block side suction passages are formed in the fixed block 15 so as to correspond to the first to sixth scroll side suction passages 96a to 96f, respectively. The first to sixth block side suction passages are also arranged at regular intervals in the circumferential direction of the fixed block 15. The other components of the compressor of the second comparative example, including other components of the fixed scroll 94 and the fixed block 15, are the same as those of the compressor of the first embodiment.

In the compressor of the second comparative example, the refrigerant gas in the suction chamber 17 flows to the inside of the peripheral wall main body portion 91 through each of the first to sixth block side suction passages and the corresponding one of the first to sixth scroll side suction passages 96a to 96f, and then, is sucked toward the compression chamber 49.

Here, in the compressor of the second comparative example, when the fixed scroll spiral wall 9c and the movable scroll spiral wall 11b are in contact with each other with the rotation of the movable scroll 11 at an upper right position and a lower left position relative to the discharge port 9d on a sheet of FIG. 13, the refrigerant gas does not flow so much through the second scroll side suction passage 96b and the third scroll side suction passage 96c but flows to the inside of the peripheral wall main body portion 91 mainly through the fourth scroll side suction passage 96d and the fifth scroll side suction passage 96e, and is sucked toward the compression chamber 49. At this time, the movable scroll spiral wall 11b operates so that the movable scroll spiral wall 11b pushes a part of the refrigerant gas present near the first and sixth scroll side suction passages 96a and 96f out of the inside of the peripheral wall main body portion 91. As a result, a part of the refrigerant gas inside the peripheral wall main body portion 91 easily flows back to the first scroll side suction passage 96a and the sixth scroll side suction passage 96f (see broken arrows in FIG. 13).

Thus, in the compressor of the second comparative example, although the scroll side suction passage 96 consists of six passages: the first to sixth scroll side suction passages 96a to 96f, all of the first to sixth scroll side suction passages 96a to 96f and all of the first to sixth block side suction passages are not always used for the suction of the refrigerant gas in the suction chamber 17 toward the compression chamber 49.

Then, as described above, when the refrigerant gas flows back to the first scroll side suction passage 96a and the sixth scroll side suction passage 96f, in the first scroll side suction passage 96a, a collision occurs between the refrigerant gas flowing back and the refrigerant gas flowing toward the compression chamber 49 through the first block side suction passage. Similarly, also in the sixth scroll side suction passage 96f, a collision occurs between the refrigerant gas flowing back and the refrigerant gas flowing toward the compression chamber 49 through the sixth block side suction passage. Note that in the compressor of the second comparative example, when the movable scroll 11 further rotates in the rotational direction R1 over its position illustrated in FIG. 13, the refrigerant gas easily flows back to the second scroll side suction passage 96b and the third scroll side suction passage 96c.

Thus, in the compressor of the second comparative example, even when the first to sixth scroll side suction passages 96a to 96f are formed in the fixed scroll 94 and the first to sixth block side suction passages are formed in the fixed block 15, it is difficult to increase suction efficiency in the refrigerant gas as a whole. As a result, also in the compressor of the second comparative example, it is difficult to increase compression efficiency in the refrigerant gas during the operation of the compressor.

As illustrated in graphs of FIGS. 14 and 15, in the compressor of the second comparative example, since the refrigerant gas flows back, first-order suction pulsation F31 as a whole during the operation of the compressor and second-order suction pulsation F41 as a whole during the operation of the compressor are inevitably increased as compared with the compressor of the first comparative example. For this reason, noise during the operation is increased also in the compressor in the second comparative example.

In contrast, the compressor in the first embodiment, the block side suction passage 61 consists of three passages: the first to third block side suction passages 61a to 61c, and the scroll side suction passage 71 consists of three passages: the first to third scroll side suction passages 71a to 71c. Thus, the refrigerant gas in the suction chamber 17 flows to the inside of the peripheral wall main body portion 91 through each of the first to third block side suction passages 61a to 61c and the corresponding one of the first to third scroll side suction passages 71a to 71c, and then, is sucked toward the compression chamber 49. As a result, in the compressor of the first embodiment, a flow rate of the refrigerant gas that is sucked from the suction chamber 17 toward the compression chamber 49 is suitably secured, as compared with the compressor of the first comparative example.

As illustrated in FIG. 3, in the compressor of the first embodiment, when the fixed scroll spiral wall 9c and the movable scroll spiral wall 11b are in contact with each other at the positions illustrated in FIG. 3 with the rotation of the movable scroll 11, the refrigerant gas flows to the inside of the peripheral wall main body portion 91 through the third scroll side suction passage 71c, and then, is sucked toward the compression chamber 49. Here, in the compressor of the first embodiment, the first to third scroll side suction passages 71a to 71c are not disposed opposite to each other at the 180 degrees in the circumferential direction of the fixed scroll 9 in the fixed scroll peripheral wall 9b of the fixed scroll 9. In the compressor of the first embodiment, this makes the refrigerant gas inside the peripheral wall main body portion 91 difficult to flow back to the first scroll side suction passage 71a, and the like, as compared with the compressor of the second comparative example.

Thus, also in the compressor of the first embodiment, a part of the refrigerant gas inside the peripheral wall main body portion 91 is not completely prevented from flowing back to the first scroll side suction passage 71a, the second scroll side suction passage 71b, or the third scroll side suction passage 71c with the rotation of the movable scroll 11. However, as compared with the compressor of the second comparative example, it may be suppressed as much as possible in the compressor of the first embodiment that a part of the refrigerant gas inside the peripheral wall main body portion 91 flows back to the first scroll side suction passage 71a, the second scroll side suction passage 71b, or the third scroll side suction passage 71c.

Accordingly, in the compressor of the first embodiment, a collision between the refrigerant gas flowing back and the refrigerant gas flowing from the suction chamber 17 toward the compression chamber 49 hardly occurs in the first to third scroll side suction passages 71a to 71c. Even when the collision between the refrigerant gas flowing back and the refrigerant gas flowing from the suction chamber 17 toward the compression chamber 49 occurs, an effect by the collision may be reduced. As a result, in the compressor of the first embodiment, the flow rate of the refrigerant gas that is sucked from the suction chamber 17 to the compression chamber 49 is sufficiently secured by the first to third block side suction passages 61a to 61c and the first to third scroll side suction passages 71a to 71c.

As indicated by black arrows in a graph of FIG. 5, also in the compressor of the first embodiment, an orientation of a vector of first-order suction pulsation in the first scroll side suction passage 71a during the operation of the compressor, an orientation of a vector of first-order suction pulsation in the second scroll side suction passage 71b during the operation of the compressor, and an orientation of a vector of first-order suction pulsation in the third scroll side suction passage 71c during the operation of the compressor are different from each other. Accordingly, the first-order suction pulsation in the first scroll side suction passage 71a, the first-order suction pulsation in the second scroll side suction passage 71b, and the first-order suction pulsation in the third scroll side suction passage 71c are operated so that they cancel out each other. As a result, also in the compressor of the first embodiment, as indicated by a white arrow in FIG. 5, a vector of first-order suction pulsation F10 as a whole during the operation of the compressor has small magnitude. Thus, in the compressor of the first embodiment, the first-order suction pulsation F10 as a whole during the operation of the compressor is suitably suppressed.

Furthermore, as indicated by black arrows in a graph of FIG. 6, in the compressor of the first embodiment, an orientation of a vector of second-order suction pulsation in the first scroll side suction passage 71a during the operation of the compressor, an orientation of a vector of second-order suction pulsation in the second scroll side suction passage 71b during the operation of the compressor, and an orientation of a vector of second-order suction pulsation in the third scroll side suction passage 71c during the operation of the compressor are different from each other. As a result, in the compressor of the first embodiment, as indicated by a white arrow in FIG. 6, a vector of second-order suction pulsation F20 as a whole during the operation of the compressor has small magnitude. That is, in the compressor of the first embodiment, the second-order suction pulsation F20 as a whole during the operation of the compressor also may be reduced. As described above, in the compressor of the first embodiment, both the first-order suction pulsation F10 and the second-order suction pulsation F20 during the operation of the compressor may be reduced, so that noise during the operation of the compressor is suitably suppressed.

Therefore, the compressor of the first embodiment is superior in compression efficiency in the refrigerant gas and has high quietness.

In particular, in this compressor, the first angle θ1 corresponding to the distance between the first scroll side suction passage 71a and the second scroll side suction passage 71b in the rotational direction R1 of the driving shaft 5, the second angle θ2 corresponding to the distance between the second scroll side suction passage 71b and the third scroll side suction passage 71c in the rotational direction R1 of the driving shaft 5, and the third angle θ3 corresponding to the distance between the first scroll side suction passage 71a and the third scroll side suction passage 71c in the direction opposite to the rotational direction R1 of the driving shaft 5 are each different from 120 degrees. Thus, the second-order suction pulsation F20 during the operation of the compressor is suitably suppressed also by not arranging the first to third scroll side suction passages 71a to 71c at regular intervals in the circumferential direction of the fixed scroll 9.

Here, in this compressor, the block side suction passage 61 consists of the first to third block side suction passages 61a to 61c, and the scroll side suction passage 71 consists of the first to third scroll side suction passages 71a to 71c. Thus, in this compressor, as compared with a case where four or more block side suction passages are formed in the block main body 15a of the fixed block 15, the block main body 15a may be reduced in diameter as much as possible while securing areas where the first to third block side suction passages 61a to 61c are formed. Similarly, in this compressor, as compared with a case where four or more scroll side suction passages are formed in the fixed scroll peripheral wall 9b of the fixed scroll 9, the fixed scroll peripheral wall 9b may be reduced in diameter as much as possible while securing areas where the first to third scroll side suction passages 71a to 71c are formed. As a result, this compressor may also be decreased in size.

In this compressor, the refrigerant gas flowing from the suction chamber 17 through the block side suction passage 61 is directly sucked toward the inside of the fixed scroll peripheral wall 9b, and by extension, toward the compression chamber 49 through the scroll side suction passage 71. Thus, in this compressor, there is no need to form a space between the second peripheral wall 14b of the compressor housing 14 and the fixed scroll peripheral wall 9b of the fixed scroll 9 for storing the refrigerant gas flowing through the block side suction passage 61. Also in this respect, this compressor may be decreased in size.

Second embodiment

As illustrated in FIG. 7, in the compressor of the second embodiment, a block side suction passage 63 is formed in the block main body 15a of the fixed block 15. Similarly to the block side suction passage 61 in the compressor of the first embodiment, the block side suction passage 63 consists of a first block side suction passage 63a, a second block side suction passage 63b, and a third block side suction passage 63c.

The first to third block side suction passages 63a to 63c are disposed inside the third bolt holes 53 in the radial direction of the fixed block 15 in the block main body 15a. The first to third block side suction passages 63a to 63c are each disposed between adjacent two of the third bolt holes 53.

The first block side suction passage 63a is formed so as to correspond to a first scroll side suction passage 73a, which will be described later. The second block side suction passage 63b is formed so as to correspond to a second scroll side suction passage 73b, which will be described later. The third block side suction passage 63c is formed so as to correspond to a third scroll side suction passage 73c, which will be described later.

The first to third block side suction passages 63a to 63c are each formed in an elongated hole shape extending in the circumferential direction of the block main body 15a. Here, shapes of the first to third block side suction passages 63a to 63c also correspond to shapes of the first to third scroll side suction passages 73a to 73c. The first to third block side suction passages 63a to 63c are arranged at respective predetermined distances from each other in the circumferential direction of the block main body 15a. Here, the first to third block side suction passages 63a to 63c are arranged at distances different from the distances between the first to third block side suction passages 61a to 61c in the compressor of the first embodiment. The arrangement of the first to third block side suction passages 63a to 63c will be described later in detail.

In this compressor, as illustrated in FIG. 8, a scroll side suction passage 73 is recessed in the fixed scroll peripheral wall 9b of the fixed scroll 9. Similarly to the scroll side suction passage 71 in the compressor of the first embodiment, the scroll side suction passage 73 consists of the first scroll side suction passage 73a, the second scroll side suction passage 73b, and the third scroll side suction passage 73c. Thus, also in this compressor, the first to third scroll side suction passages 73a to 73c, that is, the scroll side suction passage 73 is located outside the fixed scroll spiral wall 9c in the radial direction of the fixed scroll 9 and inside the fourth bolt holes 54 in the radial direction of the fixed scroll 9.

The first to third scroll side suction passages 73a to 73c open in the flange portion 92 and extend rearward from the flange portion 92 toward the peripheral wall main body portion 91 in the direction in which the driving axis O extends. The first to third scroll side suction passages 73a to 73c are each formed in a substantially rectangular hole shape extending in the circumferential direction of the fixed scroll 9. Note that as long as the first to third scroll side suction passages 73a to 73c also extend rearward in the direction in which the driving axis O extends, their shapes and sizes may be designed as appropriate.

These first to third scroll side suction passages 73a to 73c are arranged at respective predetermined distances from each other in the circumferential direction of the fixed scroll 9. More specifically, in the rotational direction R1 of the driving shaft 5, the first scroll side suction passage 73a, the second scroll side suction passage 73b, and the third scroll side suction passage 73c are arranged in this order. In addition, the scroll side suction passages 73a to 73c are each disposed between adjacent two of the fourth bolt holes 54.

Here, a portion of the fixed scroll peripheral wall 9b of the fixed scroll 9 opposite to the first scroll side suction passage 73a across the driving axis O is defined as a first specific region X11. A portion of the fixed scroll peripheral wall 9b opposite to the second scroll side suction passage 73b across the driving axis O is defined as a second specific region X12. A portion of the fixed scroll peripheral wall 9b opposite to the third scroll side suction passage 73c across the driving axis O is defined as a third specific region X13.

In this compressor, the second scroll side suction passage 73b and the third scroll side suction passage 73c are each located away from the first specific region X11 in the circumferential direction of the fixed scroll 9. The third scroll side suction passage 73c and the first scroll side suction passage 73a are each located away from the second specific region X12 in the circumferential direction of the fixed scroll 9. The first scroll side suction passage 73a and the second scroll side suction passage 73b are each located away from the third specific region X13 in the circumferential direction of the fixed scroll 9.

With this configuration, in this compressor, neither the second scroll side suction passage 73b nor the third scroll side suction passage 73c is disposed opposite to the first scroll side suction passage 73a at 180 degrees in the circumferential direction of the fixed scroll 9. Neither the third scroll side suction passage 73c nor the first scroll side suction passage 73a is disposed opposite to the second scroll side suction passage 73b at 180 degrees in the circumferential direction of the fixed scroll 9. Neither the first scroll side suction passage 73a nor the second scroll side suction passage 73b is disposed opposite to the third scroll side suction passage 73c at 180 degrees in the circumferential direction of the fixed scroll 9.

As illustrated in FIG. 9, in this compressor, a first imaginary line L11 extending straight through a center of the first scroll side suction passage 73a and the driving axis O, a second imaginary line L12 extending straight through a center of the second scroll side suction passage 73b and the driving axis O, and a third imaginary line L13 extending straight through a center of the third scroll side suction passage 73c and the driving axis O are defined in the fixed scroll 9. An angle between the first imaginary line L11 and the second imaginary line L12 in the rotational direction R1 of the driving shaft 5 is defined as a first angle θ11. An angle between the second imaginary line L12 and the third imaginary line L13 in the rotational direction R1 of the driving shaft 5 is defined as a second angle θ12. An angle between the first imaginary line L11 and the third imaginary line L13 in the direction opposite to the rotational direction R1 of the driving shaft 5 is defined as a third angle θ13.

That is, the first angle θ11 corresponds to a distance between the first scroll side suction passage 73a and the second scroll side suction passage 73b in the rotational direction R1 of the driving shaft 5. Similarly, the second angle θ12 corresponds to a distance between the second scroll side suction passage 73b and the third scroll side suction passage 73c in the rotational direction R1 of the driving shaft 5. Similarly, the third angle θ13 corresponds to a distance between the first scroll side suction passage 73a and the third scroll side suction passage 73c in the direction opposite to the rotational direction R1 of the driving shaft 5.

Here, the first angle θ11, the second angle θ12, and the third angle θ13 are all different from 120 degrees. As a result, also in this compressor, the first to third scroll side suction passages 73a to 73c are not arranged at regular intervals in the circumferential direction of the fixed scroll 9 in the fixed scroll peripheral wall 9b. The first angle θ11 is different from the first angle θ1 in the compressor of the first embodiment. Similarly, the second angle θ12 is different from the second angle θ2 in the compressor of the first embodiment. Similarly, the third angle θ13 is different from the third angle θ3 in the compressor of the first embodiment. In particular, in this compressor, the third angle θ13 is smaller than the third angle θ3 in the compressor of the first embodiment, and smaller than 120 degrees.

As described above, the first to third block side suction passages 63a to 63c illustrated in FIG. 7 are formed so as to correspond to the first to third scroll side suction passages 73a to 73c, respectively. Accordingly, the first to third block side suction passages 63a to 63c are not arranged at regular intervals in the circumferential direction of the fixed block 15. An angle between the first block side suction passage 63a and the third block side suction passage 63c in the direction opposite to the rotational direction R1 of the driving shaft 5 is smaller than 120 degrees. The other components of this compressor are the same as those of the compressor of the first embodiment.

In this compressor, the first to third scroll side suction passages 73a to 73c are not disposed opposite to each other at the 180 degrees in the circumferential direction of the fixed scroll 9 in the fixed scroll peripheral wall 9b of the fixed scroll 9. Accordingly, it is suppressed as much as possible also in this compressor that a part of the refrigerant gas inside the peripheral wall main body portion 91 flows back to the first scroll side suction passage 73a, the second scroll side suction passage 73b, or the third scroll side suction passage 73c. As a result, also in this compressor, a flow rate of the refrigerant gas that is sucked from the suction chamber 17 to the compression chamber 49 is sufficiently secured by the first to third block side suction passages 63a to 63c and the first to third scroll side suction passages 73a to 73c.

In particular, as illustrated in FIG. 8, in this compressor, the second scroll side suction passage 73b is located just below the discharge port 9d in the fixed scroll peripheral wall 9b. Accordingly, in this compressor, when the fixed scroll spiral wall 9c and the movable scroll spiral wall 11b are in contact with each other with the rotation of the movable scroll 11 at an upper right position and a lower left position relative to the discharge port 9d on a sheet of FIG. 8, the refrigerant gas flows from the second scroll side suction passage 73b through both the outside and the inside of the movable scroll spiral wall 11b, and then, is sucked toward the inside of the peripheral wall main body portion 91, and by extension, toward the compression chamber 49 (see broken arrows in FIG. 8). Thus, in this compressor, the flow rate of the refrigerant gas that is sucked from the suction chamber 17 to the compression chamber 49 is more suitably secured by the first to third block side suction passages 63a to 63c and the first to third scroll side suction passages 73a to 73c. Other operation of this compressor is the same as that of the compressor in the first embodiment.

In the above description, the present disclosure has been described based on the first embodiment and the second embodiment. However, the present disclosure is not limited to the above-described first embodiment and the second embodiment, and may be modified as appropriate within the scope of the present disclosure.

For example, in the compressor of the first embodiment, the first to third scroll side suction passages 71a to 71c may be disposed at regular intervals in the circumferential direction of the fixed scroll 9. The same goes for the compressor of the second embodiment.

In the compressor of the first embodiment, one of the first to third angles θ1 to θ3 may be 120 degrees. The same goes for the compressor of the second embodiment.

In the compressor of the first embodiment, instead of the gasket plate 24, liquid gasket may be applied to a front end of the second peripheral wall 14b or a rear end of the flange portion 92 or an O-ring, or the like, may be provided between the second peripheral wall 14b and the flange portion 92. The same goes for the compressor of the second embodiment.

In the compressor of the first embodiment, the number of each of the first to sixth bolt holes 51 to 56 is six. However, the present disclosure is not limited thereto, and the number of each of the first to sixth bolt holes 51 to 56 may be designed as appropriate. The same goes for the compressor of the second embodiment.

In the compressor of the first embodiment, the balance weight 6a is formed integrally with the bushing 6. However, the present disclosure is not limited thereto. The present disclosure may have a configuration in which the balance weight 6a is formed in the large diameter portion 5b of the driving shaft 5 and the balance weight 6a is disposed in front of the fixed block 15 with the driving shaft 5 inserted through the fixed block 15. The same goes for the compressor of the second embodiment.

Industrial Applicability

The present disclosure may be used for an air conditioner of a vehicle, or the like.

Claims

1. A scroll compressor comprising:

a housing including a suction chamber into which fluid is sucked;

a driving shaft provided in the housing, the driving shaft being rotatable around a driving axis;

a fixed scroll fixed to the housing; and

a movable scroll provided in the housing, the movable scroll being connected to the driving shaft,

the housing having a fixed block that is located between the suction chamber and a set of the fixed scroll and the movable scroll, and through which the driving shaft is rotatably inserted,

the movable scroll and the fixed block being coupled to each other by an anti-rotation mechanism that prevents the movable scroll from rotating on an axis of the movable scroll, and

the fluid being compressed in a compression chamber by the movable scroll orbiting relative to the fixed scroll, the compression chamber being formed between the fixed scroll and the movable scroll, wherein

the fixed block has a block side suction passage that communicates with the suction chamber and through which the fluid in the suction chamber flows toward the fixed scroll,

the fixed scroll has a scroll side suction passage that is recessed in a direction in which the driving axis extends, that faces the block side suction passage in the direction in which the driving axis extends and communicates with the block side suction passage, and through which the fluid is sucked from the block side suction passage toward the compression chamber,

the block side suction passage consists of a first block side suction passage, a second block side suction passage, and a third block side suction passage that are arranged away from each other in a rotational direction of the driving shaft,

the scroll side suction passage consists of a first scroll side suction passage that communicates with the first block side suction passage, a second scroll side suction passage that is located away from the first scroll side suction passage in the rotational direction of the driving shaft and communicates with the second block side suction passage, and a third scroll side suction passage that is located away from the first scroll side suction passage and the second scroll side suction passage in the rotational direction of the driving shaft and communicates with the third block side suction passage,

a portion of the fixed scroll opposite to the first scroll side suction passage across the driving axis is defined as a first specific region,

a portion of the fixed scroll opposite to the second scroll side suction passage across the driving axis is defined as a second specific region, and

the second scroll side suction passage and the third scroll side suction passage are located away from the first specific region in a circumferential direction of the fixed scroll, and the third scroll side suction passage is located away from the second specific region in the circumferential direction of the fixed scroll.

2. The scroll compressor according to claim 1, wherein the first scroll side suction passage, the second scroll side suction passage, and the third scroll side suction passage are arranged in this order in the rotational direction of the driving shaft, a first imaginary line extending straight through a center of the first scroll side suction passage and the driving axis, a second imaginary line extending straight through a center of the second scroll side suction passage and the driving axis, and a third imaginary line extending straight through a center of the third scroll side suction passage and the driving axis are defined in the fixed scroll, an angle between the first imaginary line and the second imaginary line in the rotational direction of the driving shaft is defined as a first angle, an angle between the second imaginary line and the third imaginary line in the rotational direction of the driving shaft is defined as a second angle, an angle between the first imaginary line and the third imaginary line in the rotational direction of the driving shaft is defined as a third angle, and at least two of the first angle, the second angle, and the third angle are each different from 120 degrees.