JP2010190074A - Scroll type fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a scroll type fluid machine for compatibly attaining a small number of components and high sealing performance while easily achieving a smaller size and securing strength. <P>SOLUTION: The scroll type fluid machine includes a drive mechanism which consists of a driving shaft 13 provided rotatable around a first axis O1, an eccentric pin 16 provided integrally rotatable with the driving shaft 13 and having an outer peripheral face 16a formed into a cylindrical shape with a second axis O2 as a center axis, and a bearing device 18 having an outer peripheral face 18d fixed to a movable scroll 9 and an inner peripheral face 18e abutting on the outer peripheral face 16a of the eccentric pin 16 and rotatable around a third axis O3. The first axis O1, the second axis O2 and the third axis O3 are parallel and eccentric to one another. The first axis O1, the second axis O2 and the third axis O3 are set so that the eccentric pin 16 can impart thrust to the bearing device 18 through the rotation of the driving shaft 13. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a scroll type fluid machine.

  Conventionally, scroll type fluid machines disclosed in Patent Documents 1 and 2 are known. These scroll type fluid machines support a fixed scroll, a movable scroll meshing with the fixed scroll, a drive mechanism for driving the movable scroll to revolve with respect to the fixed scroll, and a non-rotatable support for the movable scroll with respect to the fixed scroll. And a rotation prevention mechanism.

  The drive mechanism of the scroll type fluid machine disclosed in Patent Document 1 is formed in a cylindrical shape with a drive shaft provided rotatably around a first axis, a rotary shaft provided integrally with the drive shaft, and having a second axis as a central axis. And an eccentric pin having an outer peripheral surface. The first axis and the second axis are parallel to each other and are eccentric from each other. Further, this drive mechanism has a cylindrical bearing device around the eccentric pin. The rotation center of the bearing device is also the second shaft. The outer peripheral surface of the bearing device is fixed to the movable scroll, and the inner peripheral surface of the bearing device is in contact with the outer peripheral surface of the eccentric pin and is rotatable around the second axis.

  In the scroll type fluid machine employing this driving mechanism, the eccentric shaft pivots around the first axis when the driving shaft is driven to rotate around the first axis, and the movable scroll is connected to the bearing device and the rotation prevention mechanism. Revolve around the second axis by cooperation. Further, this scroll type fluid machine does not have the bush disclosed in Patent Document 2 described later, and therefore has an advantage that the number of parts is small.

  Also, the drive mechanism of the scroll type fluid machine disclosed in Patent Document 2 is also provided with a drive shaft that is rotatable around the first axis, and a cylinder that is rotatable with the drive shaft and that has the second axis as the central axis. And an eccentric pin having an outer peripheral surface formed in a shape. The first axis and the second axis in this drive mechanism are parallel to each other and are eccentric from each other. This drive mechanism has a bush around the eccentric pin and a bearing device around the bush. The rotation center of the bush and the bearing device is a third axis that is parallel to the first axis and the second axis and is eccentric from the first axis and the second axis. The outer peripheral surface of the bearing device is fixed to the movable scroll, the inner peripheral surface of the bearing device is in contact with the outer peripheral surface of the bush, and the inner peripheral surface of the bush is in contact with the outer peripheral surface of the eccentric pin and can rotate around the third axis. It has become. The first shaft, the second shaft, and the third shaft are set such that the eccentric pin and the bush can apply a pressing force to the bearing device by the rotation of the drive shaft.

  In the scroll type fluid machine employing this drive mechanism, the drive shaft is driven to rotate around the first axis, whereby the eccentric pin pivots around the first axis, and the bush is allowed to swing around the second axis. While turning around the first axis. The movable scroll revolves around the third axis in cooperation with the bearing device and the rotation prevention mechanism. At this time, since the eccentric pin and the bush apply a pressing force to the bearing device, the sealing performance between the fixed scroll and the movable scroll is improved.

Japanese Utility Model Publication No. 57-204401 JP 61-8403 A

  However, the double-scroll type fluid machine can exhibit only the selective effects of a small number of parts and high sealing performance, and cannot achieve both of these effects.

  Further, when the drive mechanism disclosed in Patent Document 2 is employed to ensure high sealing performance, a bush and a bearing device need to be provided between the eccentric pin and the movable scroll. The eccentric pin must be designed to be thin, and it is difficult to ensure the strength of the eccentric pin.

  The present invention has been made in view of the above-described conventional situation, and provides a scroll type fluid machine that can achieve both a small number of parts and a high sealing performance, and can easily achieve downsizing and ensuring strength. This is a problem to be solved.

The scroll type fluid machine of the present invention includes a fixed scroll, a movable scroll meshing with the fixed scroll, a drive mechanism for driving the movable scroll to revolve with respect to the fixed scroll, and the movable scroll with respect to the fixed scroll. In a scroll type fluid machine provided with a rotation prevention mechanism that supports the rotation of
The drive mechanism includes a drive shaft provided rotatably around a first axis;
An eccentric pin provided so as to be integrally rotatable with the drive shaft, and having an outer peripheral surface formed in a cylindrical shape having a second axis that is parallel to the first axis and eccentric from the first axis as a central axis;
An outer peripheral surface is fixed to the movable scroll, an inner peripheral surface is in contact with the outer peripheral surface of the eccentric pin, is parallel to the first axis and the second axis, and is eccentric from the first axis and the second axis. And a bearing device rotatable around the third axis,
The first shaft, the second shaft, and the third shaft are set such that the eccentric pin can apply a pressing force to the bearing device by the rotation of the drive shaft (Claim 1). .

  In the scroll type fluid machine of the present invention, the eccentric pin pivots around the first axis as the drive shaft rotates around the first axis. The movable scroll revolves around the third axis in cooperation with the bearing device and the rotation prevention mechanism. At this time, since the eccentric pin applies a pressing force to the bearing device, the sealing performance between the fixed scroll and the movable scroll is improved. Further, this scroll type fluid machine does not have a conventional bush, and therefore has an advantage that the number of parts is small.

  Further, since the scroll type fluid machine of the present invention does not require a conventional bushing between the eccentric pin and the movable scroll, the eccentric pin can be designed to be thick even in a small scroll type fluid machine. It is easy to ensure the strength.

  Therefore, according to the scroll type fluid machine of the present invention, it is possible to achieve both a small number of parts and a high sealing performance, and to easily achieve downsizing and ensuring strength. For this reason, the scroll type fluid machine can be easily reduced in weight and reduced in size and can be mounted on a vehicle or the like, and can be easily manufactured to reduce the manufacturing cost. Is possible.

  The scroll type fluid machine of the present invention may include a counterweight having a center of gravity on an extension line from the third axis toward the first axis. The drive shaft, the eccentric pin, and the counterweight can be integrated (claim 2). In this case, the number of parts can be further reduced. The counterweight plays a role of canceling the centrifugal force accompanying the revolution of the movable scroll.

  In the scroll type fluid machine of the present invention, the eccentric pin and the counterweight can be integrally fixed to the drive shaft. In this case, the components constituting the eccentric pin and the counterweight are manufactured separately from the drive shaft, and the number of types of the components is increased to enable the manufacture of various types of scroll fluid machines. The increase in manufacturing cost can be minimized while maintaining versatility.

1 is a cross-sectional view of a scroll compressor according to Embodiment 1. FIG. FIG. 3 is an enlarged cross-sectional view of a main part of the scroll compressor according to Embodiment 1. BRIEF DESCRIPTION OF THE DRAWINGS FIG. FIG. 3 is an enlarged front view of a main part of the scroll compressor according to the first embodiment. It is an expanded sectional view of the principal part concerning the scroll compressor of Example 2. FIG.

  Embodiments 1 and 2 in which the present invention is embodied in a scroll compressor will be described below with reference to the drawings.

Example 1
As shown in FIG. 1, the compressor according to the first embodiment includes a housing 3 including a bottomed cylindrical front housing 1 and a lid-like rear housing 2. A shaft support member 4 is provided in the front housing 1, and a fixed scroll 5 is provided behind the shaft support member 4. While the front housing 1 and the rear housing 2 are housed in a state in which the shaft support member 4 and the fixed scroll 5 are in contact with each other, the rear end of the front housing 1 and the front end of the rear housing 2 are abutted with each other, and the bolt 6 Are fixed to each other. The front housing 1 and the shaft support member 4 form a suction chamber 7, and the fixed scroll 5 and the rear housing 2 form a discharge chamber 8.

  The shaft support member 4 includes a cylindrical main body portion 4a and a flange portion 4b projecting outward from the opening edge of the rear end of the main body portion 4a. A shaft hole 4c is formed through the center of the main body 4a. 4b is brought into contact with a step 1a formed on the inner peripheral surface of the front housing 1 and stopped in front. Three or more rotation prevention pins 10a for restricting the rotation of a movable scroll 9, which will be described later, are fixed to the rear end portion of the shaft support member 4.

  A bearing device 11 is provided in the center of the inner surface of the bottom wall 1 b of the front housing 1, and a bearing device 12 is provided in the main body 4 a of the shaft support member 4. A drive shaft 13 extending in the axial direction in the front and rear directions is supported on the bearing devices 11 and 12 so as to be rotatable around the first axis O1. A sealing material 14 for sealing is interposed between the shaft support member 4 and the drive shaft 13 by a circlip 15.

  A cylindrical eccentric pin 16 is formed at the rear end of the drive shaft 13 so as to protrude rearward. As shown in FIGS. 2-4, the outer peripheral surface 16a of the eccentric pin 16 is formed in the cylindrical shape which makes the 2nd axis | shaft O2 the central axis. The second axis O2 is parallel to the first axis O1 and is eccentric from the first axis O1.

  Further, as shown in FIG. 1, a fan-shaped counterweight 17 is formed at the rear end of the drive shaft 13 so as to bulge in the radial direction. As shown in FIG. 2, the drive shaft 13, the eccentric pin 16, and the counterweight 17 are integrated.

  As shown in FIG. 1, the fixed scroll 5 includes a fixed-side substrate 5c having a bottomed cylindrical shape by a base wall 5a and an outer peripheral wall 5b, and a fixed raised up on the front surface of the base wall 5a inside the outer peripheral wall 5b. It comprises a side spiral wall 5d.

  On the other hand, the movable scroll 9 is engaged with the fixed scroll 5. The movable scroll 9 includes a disk-shaped movable substrate 9a and a movable spiral wall 9b raised on the rear surface of the movable substrate 9a.

  As shown in FIG. 2, a boss 9 c protruding forward is formed on the movable side substrate 9 a of the movable scroll 9. The inner peripheral surface 9d of the boss 9c is formed in a cylindrical shape having the third axis O3 as a central axis. The third axis O3 is parallel to the first axis O1 and the second axis O2, and is eccentric from the first axis O1 and the second axis O2.

  A bearing device 18 is provided between the eccentric pin 16 and the boss 9 c of the movable scroll 9. The bearing device 18 includes an outer ring 18a, balls 18b, an inner ring 18c, and a cage (not shown). The outer peripheral surface 18d of the outer ring 18a is fixed to the inner peripheral surface 9d of the boss 9c by press fitting or the like. The inner peripheral surface 18e of the inner ring 18c is in contact with the outer peripheral surface 16a of the eccentric pin 16 in line contact. The inner ring 18c of the bearing device 18 is rotatable around the third axis O3.

  The drive shaft 13, the eccentric pin 16, and the bearing device 18 constitute a drive mechanism. As shown in FIGS. 3 and 4, the third axis O3 is eccentric from the first axis O1 in the first direction (upward in the drawing). The second axis O2 is eccentric from the first axis O1 and the third axis O3 in the second direction (upper right direction in the figure). The eccentric pin 16 rotates around the first axis O1 in a direction (right direction in the drawing) in which the second axis O2 is located with respect to the third axis O3. The center of gravity C1 of the counterweight 17 exists on an extension line from the third axis O3 toward the first axis O1.

  As shown in FIG. 1, the fixed scroll 5 and the movable scroll 9 are engaged with each other via the spiral walls 5d and 9b, and the tips of the spiral walls 5d and 9b slide on the mating substrates 5c and 9a. It is configured to be possible. As shown in FIG. 2, three or more rotation prevention holes 10b for receiving the tip of the rotation prevention pin 10a in a loosely fitted state are formed in the front surface of the movable substrate 9a. A cylindrical ring 10c is loosely fitted in each rotation prevention hole 10b, and each rotation prevention pin 10a slides and rolls on the inner peripheral surface of the ring 10c. The rotation prevention hole 10b, the ring 10c and the rotation prevention pin 10a constitute a rotation prevention mechanism.

  As shown in FIG. 1, a compression chamber 19 is formed between the fixed side substrate 5c and the fixed side spiral wall 5d and the movable side substrate 9a and the movable side spiral wall 9b. Further, the drive shaft 13 is located on the front side of the movable side substrate 9a (the back side opposite to the compression chamber 19 with the movable side substrate 9a interposed therebetween) and between the movable side substrate 9a and the shaft support member 4. A back pressure chamber 20 facing the rear end is formed. Further, a suction region 21 is formed between the shaft support member 4, the outer peripheral wall 5b, and the outermost peripheral part of the movable spiral wall 9b.

  The suction chamber 7 and the suction area 21 in the front housing 1 communicate with each other by a suction passage 22 formed in the lower part of the front housing 1. In the suction chamber 7, a stator 23 is fixed to the inner peripheral surface of the front housing 1, and a rotor 24 is fixed to the drive shaft 13 inside the stator 23. The rotor 24, the stator 23, and the drive shaft 13 constitute a motor mechanism, and the drive shaft 13 and the rotor 24 are integrally rotated by energizing the stator 23.

  Further, a suction port 1c connected to an evaporator (not shown) by a pipe is formed through the front end side of the peripheral wall of the front housing 1 so as to penetrate therethrough. The evaporator is connected to the expansion valve and the condenser by piping. The compressor, the evaporator, the expansion valve, and the condenser constitute a refrigeration circuit of the vehicle air conditioner. A low-pressure and low-temperature refrigerant gas or the like in the refrigeration circuit is supplied from the suction port 1 c into the suction region 21 through the suction chamber 7 and the suction passage 22.

  A discharge chamber 8 is formed between the rear end of the fixed side substrate 5 c and the front end of the rear housing 2. A discharge port 5e is formed through the center of the fixed substrate 5c, and the compression chamber 19 and the discharge chamber 8 communicate with each other via the discharge port 5e. Further, a discharge valve (not shown) for opening and closing the discharge port 5e and a retainer 25 for regulating the opening degree of the discharge valve are provided in the discharge chamber 8 at the rear end of the fixed side substrate 5c.

  In the rear housing 2, an oil separation chamber 2 a is formed behind the discharge chamber 8 so as to extend in the vertical direction while being mounted on the vehicle. A partition wall 2b is provided between the oil separation chamber 2a and the discharge chamber 8, and a discharge hole 2c that connects the oil separation chamber 2a and the discharge chamber 8 is formed through the partition wall 2b. An oil separator 26 for separating the lubricating oil contained in the refrigerant gas is provided in the oil separation chamber 2a. The oil separator 26 has a cylindrical shape and is accommodated in the oil separation chamber 2a in a fitted state. The refrigerant gas introduced into the oil separation chamber 2a from the discharge chamber 8 through the discharge hole 2c separates the lubricating oil by centrifugal separation by the oil separator 26, and the separated lubricating oil falls and is stored in the oil separation chamber 2a. It is like that. An upper end of the oil separation chamber 2a located above the oil separator 26 is a discharge port 2d, and the discharge port 2d is connected to a condenser of the refrigeration circuit by a pipe.

  The lower end of the oil separation chamber 2a and the lower end of the discharge chamber 8 communicate with each other through an oil supply port 2e, and the lower end of the discharge chamber 8 communicates with the back pressure chamber 20 through an air supply passage 27. The air supply passage 27 is formed in a communication hole 27 a penetrating the outer peripheral wall 5 b of the fixed scroll 5 and a plate 28 interposed between the shaft support member 4 and the movable scroll 9, and has an arc shape up to the back pressure chamber 20. And a slit 27b extending in the direction. The supply passage 27 supplies the high-pressure refrigerant gas in the discharge chamber 8 to the back pressure chamber 20 together with the lubricating oil.

  The compressor configured as described above operates as follows. That is, when the drive shaft 13 shown in FIGS. 1 and 2 is rotationally driven by the operation of the vehicle driver, as shown in FIGS. 3 and 4, the eccentric pin 16 is moved in the direction R around the first axis O1. Turn. At this time, when the outer peripheral surface 16a of the eccentric pin 16 slides and rolls along the inner peripheral surface 18e of the inner ring 18c of the bearing device 18, the inner ring 18c turns while rotating around the third axis O3, and the outer ring 18a turns around the third axis O3. The rotation prevention pin 10a slides and rolls along the inner peripheral surface of the ring 10c, and the ring 10c slides and rolls along the inner peripheral surface of the rotation prevention hole 10b. The movable scroll 9 revolves around the third axis O3. During this time, the counterweight 17 plays a role of canceling out the centrifugal force accompanying the revolution of the movable scroll 9.

  Then, the revolution of the movable scroll 9 causes the compression chamber 19 to move from the outer peripheral side of the scroll walls 5d, 9b of the scrolls 5, 9 to the center while reducing the volume. For this reason, the refrigerant gas or the like is taken into the suction region 21 from the evaporator through the suction port 1c through the suction chamber 7 and the suction passage 22, and further sucked into the compression chamber 19 from the suction region 21 and compressed. The refrigerant gas or the like compressed to the discharge pressure is discharged from the discharge port 5e to the discharge chamber 8 and taken into the oil separation chamber 2a through the discharge hole 2c, where the lubricating oil is separated. The lubricating oil separated from the refrigerant gas falls from the oil separator 26 and is stored in the oil separation chamber 2a. The lubricating oil stored in the oil separation chamber 2a is supplied to the back pressure chamber 20 through the supply passage 27 together with some refrigerant gas. The refrigerant gas or the like from which the lubricating oil has been separated is discharged from the oil separator 26 to the condenser through the discharge port 2d. In this way, air conditioning of the vehicle air conditioner is performed.

  At this time, as shown in FIG. 4, the rotational force F <b> 1 acts on the eccentric pin 16, and the rotational force F <b> 1 contributes to the compression work of the refrigerant gas in the compression chamber 19. For this reason, the eccentric pin 16 receives a compression reaction force F1 'in a direction opposite to the rotational force F1. A driving force F2 from the third axis O3 toward the second axis O2 acts on the eccentric pin 16. The eccentric pin 16 applies a pressing force F3 to the bearing device 18 due to the difference between the driving force F2 and the rotational force F1. For this reason, in this compressor, the sealing performance between the fixed scroll 5 and the movable scroll 9 is improved. Moreover, since this compressor does not have a conventional bush, it has an advantage that the number of parts is small.

  Moreover, since this compressor does not need to provide a conventional bush between the eccentric pin 16 and the movable scroll 9, the eccentric pin 16 can be designed thick even if it is small. For this reason, it is easy to ensure the strength of the eccentric pin 16.

  Therefore, according to this compressor, it is possible to achieve both a small number of parts and high sealing performance, and to easily achieve downsizing and ensuring strength. In particular, in this compressor, since the drive shaft 13, the eccentric pin 16, and the counterweight 17 are integrated, the number of parts can be further reduced. For this reason, the compressor can be easily reduced in weight and size and can be mounted on a vehicle.

  In addition, since this compressor does not employ a bush, the distance between the second shaft O2 and the third shaft O3 can be made relatively large, the degree of freedom in design can be increased, and the stacking tolerance can be reduced. It is. In addition, since the eccentric pin 16 can be designed to be thick, the degree of freedom in selecting the material of the drive shaft 13 is increased. For this reason, this compressor can be easily manufactured and can reduce the manufacturing cost.

(Example 2)
In the compressor of the second embodiment, as shown in FIG. 5, the parts 30 constituting the eccentric pin 30 a and the counterweight 30 b are separated from the drive shaft 29. Then, the eccentric pin 30 a and the counterweight 30 b are integrally fixed to the drive shaft 29 by fixing the component 30 to the drive shaft 29 by press fitting or the like. Other configurations are the same as those of the first embodiment.

  In this compressor, it is possible to increase the manufacturing cost to a minimum while maintaining the versatility of the drive shaft 29 while enabling the manufacture of scroll compressors of various specifications by increasing the types of parts 30. it can. Other functions and effects are the same as those of the first embodiment.

  In the above, the present invention has been described with reference to the first and second embodiments. However, the present invention is not limited to the first and second embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say. For example, the bearing device does not use a rolling element, and may be a plain bearing.

  The present invention can be used for a compressor, a pump, and the like.

DESCRIPTION OF SYMBOLS 5 ... Fixed scroll 9 ... Movable scroll 13, 16, 18 ... Drive mechanism (13 ... Drive shaft, 16 ... Eccentric pin, 18 ... Bearing apparatus)
10b, 10c, 10a ... rotation prevention mechanism (10b ... rotation prevention hole, 10c ... ring, 10a ... rotation prevention pin)
O1 ... first axis O2 ... second axis 16a ... outer peripheral surface 18d ... outer peripheral surface 18e ... inner peripheral surface O3 ... third axis 17 ... counter weight

Claims (3)

A fixed scroll, a movable scroll meshing with the fixed scroll, a drive mechanism for driving the movable scroll to revolve with respect to the fixed scroll, and a rotation prevention mechanism for supporting the movable scroll with respect to the fixed scroll so as not to rotate. In a scroll type fluid machine with
The drive mechanism includes a drive shaft provided rotatably around a first axis;
An eccentric pin provided so as to be integrally rotatable with the drive shaft, and having an outer peripheral surface formed in a cylindrical shape having a second axis that is parallel to the first axis and eccentric from the first axis as a central axis;
An outer peripheral surface is fixed to the movable scroll, an inner peripheral surface is in contact with the outer peripheral surface of the eccentric pin, is parallel to the first axis and the second axis, and is eccentric from the first axis and the second axis. And a bearing device rotatable around the third axis,
The scroll-type fluid machine, wherein the first shaft, the second shaft, and the third shaft are set such that the eccentric pin can apply a pressing force to the bearing device by the rotation of the drive shaft. A counterweight having a center of gravity on an extension line from the third axis toward the first axis;
The scroll type fluid machine according to claim 1, wherein the drive shaft, the eccentric pin, and the counterweight are integrated. A counterweight having a center of gravity on an extension line from the third axis toward the first axis;
The scroll type fluid machine according to claim 1, wherein the eccentric pin and the counterweight are integrally fixed to the drive shaft.

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