US20100209278A1

US20100209278A1 - Scroll-type fluid machine

Info

Publication number: US20100209278A1
Application number: US12/705,139
Authority: US
Inventors: Susumu Tarao; Masao Iguchi; Hidefumi Mori
Original assignee: Toyota Industries Corp
Current assignee: Toyota Industries Corp
Priority date: 2009-02-17
Filing date: 2010-02-12
Publication date: 2010-08-19
Also published as: EP2218914A2; JP2010190074A

Abstract

A scroll-type fluid machine includes a mechanism for driving a movable scroll relative to a fixed scroll. The mechanism includes a drive shaft rotatable on a first axis, an eccentric pin and a bearing. The eccentric pin revolves around the first axis with the rotation of the drive shaft and has an outer peripheral surface centered on a second axis that is parallel to and eccentric to the first axis. The bearing is mounted to the movable scroll and has an inner peripheral surface centered on a third axis that is parallel to and eccentric to the first and second axes. The inner peripheral surface is in contact with the outer peripheral surface of the eccentric pin. Pressing force is applied to the bearing from the eccentric pin due to the arrangement of the first, second and third axes so as to press the movable scroll to the fixed scroll.

Description

BACKGROUND OF THE INVENTION

The present invention relates to a scroll-type fluid machine.
Conventional scroll-type fluid machines are disclosed in, for example, Japanese Unexamined Utility Model Application Publication No. 57-204401 and Japanese Unexamined Patent Application Publication No. 61-8403. Each of the fluid machines includes fixed and movable scrolls engaged with each other, a drive mechanism for driving the movable scroll relative to the fixed scroll, and an anti-rotation mechanism for preventing the movable scroll from rotating on its own axis.
The drive mechanism disclosed in Japanese Unexamined Utility Model Application Publication No. 57-204401 includes a drive shaft rotatable on a first axis and an eccentric pin provided integrally with the drive shaft. The eccentric pin has an outer peripheral surface centered on a second axis that is parallel to and eccentric to the first axis. The drive mechanism further includes a cylindrical bearing provided around the eccentric pin. The rotational axis of the bearing is the second axis. The bearing is fixed at the outer peripheral surface thereof to the movable scroll. The inner peripheral surface of the bearing is in contact with the outer peripheral surface of the eccentric pin so that the bearing is rotatable on the second axis.
In the fluid machine with such drive mechanism, the eccentric pin revolves around the first axis with the rotation of the drive shaft on the first axis, and the movable scroll coupled to the eccentric pin through the bearing revolves around the first axis with the rotation on its own axis restricted by the anti-rotation mechanism. In the fluid machine, no bush is provided between the eccentric pin and the bearing, resulting in a reduced number of parts.
The drive mechanism disclosed in Japanese Unexamined Patent Application Publication No. 61-8403 includes a drive shaft rotatable on a first axis and an eccentric pin provided integrally with the drive shaft and having an outer peripheral surface centered on a second axis that is parallel to and eccentric to the first axis. The drive mechanism further includes a bush provided around the eccentric pin and a bearing provided around the bush. The rotational axis of the bush and the bearing is a third axis that is parallel to and eccentric to the first and second axes. The bearing is fixed at the outer peripheral surface thereof to the movable scroll. The inner peripheral surface of the bearing 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 so that the bush is rotatable on the third axis. The first, second and third axes are arranged so that the bearing receives pressing force from the eccentric pin and the bush when the drive shaft is rotated.
In the fluid machine with such drive mechanism, the eccentric pin revolves around the first axis with the rotation of the drive shaft on the first axis, and the bush revolves around the first axis with the rotation about the second axis allowed. The movable scroll coupled to the bush through the bearing revolves around the first axis with the rotation on its own axis restricted by the anti-rotation mechanism. In this case, the bearing receives pressing force from the eccentric pin and the bush, which improves sealing between the fixed scroll and the movable scroll.
However, neither of the above fluid machines allows reduced number of parts and improved sealing between the fixed and movable scrolls simultaneously.
In the drive mechanism disclosed in Japanese Unexamined Patent Application Publication No. 61-8403 wherein the bush and the bearing are provided between the eccentric pin and the movable scroll, it is difficult to provide an eccentric pin having a diameter that is large enough to ensure the strength of the eccentric pin in a small-size fluid machine.
The present invention is directed to providing a scroll-type fluid machine that allows reduced number of parts as well as improved sealing between scrolls and also provides an eccentric pin of sufficient strength in a small-size fluid machine.

SUMMARY OF THE INVENTION

In accordance with an aspect of the present invention, a scroll-type fluid machine includes a fixed scroll and a movable scroll engaged with each other, an anti-rotation mechanism for preventing the rotation of the movable scroll on its own axis, and a drive mechanism for driving the movable scroll in orbital motion relative to the fixed scroll. The drive mechanism includes a drive shaft, an eccentric pin and a bearing. The drive shaft is rotatable on a first axis. The eccentric pin revolves around the first axis with the rotation of the drive shaft. The eccentric pin has an outer peripheral surface centered on a second axis that is parallel to and eccentric to the first axis. The bearing is mounted to the movable scroll. The bearing has an inner peripheral surface centered on a third axis that is parallel to and eccentric to the first and second axes, and the inner peripheral surface is in contact with the outer peripheral surface of the eccentric pin. Pressing force is applied to the bearing from the eccentric pin due to the arrangement of the first, second and third axes so as to press the movable scroll to the fixed scroll.
Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention;

FIG. 2 is an enlarged fragmentary view of the compressor of FIG. 1;

FIG. 3 is a fragmentary elevational view of a structure around an eccentric pin of the compressor of FIG. 1;

FIG. 4 is a schematic diagram showing first, second and third axes in the compressor of FIG. 1; and

FIG. 5 is a fragmentary sectional view of a scroll compressor according to a second embodiment of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

The following will describe the embodiments of the present invention with reference to the accompanying drawings.
FIG. 1 shows a scroll compressor according to the first embodiment of the present invention. It is noted that the right-hand side and the left-hand side as viewed in FIG. 1 are the front side and the rear side of the scroll compressor, respectively, and that the upper and lower sides as viewed in FIG. 1 are the upper and lower sides of the scroll compressor when installed in place, respectively. The scroll compressor (hereinafter referred to merely as compressor) is used, for example, in a vehicle air conditioner. The compressor has a cylindrical front housing 1 the opening of which is covered by a rear housing 2. The front housing 1 and the rear housing 2 cooperate to form a housing assembly 3 that accommodates therein a shaft support 4, a fixed scroll 5 and a movable scroll 9. The fixed scroll 5 is located behind the shaft support 4. The front housing 1 and the rear housing 2 are connected to each other by using bolts 6 while keeping the shaft support 4 in contact with the fixed scroll 5. The compressor has a suction chamber 7 formed between the front housing 1 and the shaft support 4 and a discharge chamber 8 formed between the fixed scroll 5 and the rear housing 2.
The shaft support 4 has a cylindrical main body 4A and a flange 4B that extends radially outward from the rear end of the main body 4A. The main body 4A has a shaft hole 4C formed therethrough. The flange 4B is engaged with a step 1A that is formed in the inner peripheral surface of the front housing 1. The shaft support 4 has three or more pins 10A (only one is shown in the drawing) fixed to the rear end thereof for preventing rotation of the movable scroll 9 on its own axis.
The compressor has a drive shaft 13 extending in the front housing 1 in longitudinal direction of the compressor. The front portion of the drive shaft 13 is rotatably supported by a bearing 11 that is mounted at the center of the end wall 1B of the front housing 1. The rear end portion of the drive shaft 13 is rotatably supported by a bearing 12 that is mounted in the main body 4A of the shaft support 4. The drive shaft 13 is rotatable on a first axis O1. A seal member 14 is mounted on the shaft support 4 and retained by a circlip 15 for sealing between the shaft support 4 and the drive shaft 13.
The drive shaft 13 has a cylindrical eccentric pin 16 formed at the rear end thereof. Referring to FIGS. 2 through 4, the eccentric pin 16 has an outer peripheral surface 16A centered on a second axis O2 that is parallel to and eccentric to the first axis O1.
The drive shaft 13 has a sector-shaped counterweight 17 formed at the rear end thereof. The drive shaft 13, the eccentric pin 16 and the counterweight 17 are formed integrally.
As shown in FIG. 1, the fixed scroll 5 includes an end plate 5A, a side wall 5B and a scroll wall 5D. The end plate 5A cooperates with the side wall 5B to form a cylindrical base 5C of the fixed scroll 5. The scroll wall 5D is located radially inward of the side wall 5B and projects forward from the end plate 5A.
The movable scroll 9 is engaged with the fixed scroll 5. The movable scroll 9 includes a circular end plate 9A and a scroll wall 9B projecting rearward from the end plate 9A.
As shown in FIG. 2, the end plate 9A of the movable scroll 9 is formed with a cylindrical boss 9C projecting forward. The boss 9C has an inner peripheral surface 9D centered on a third axis O3 that is parallel to and eccentric to the first and second axes O1 and O2.
A bearing 18 is provided between the eccentric pin 16 and the movable scroll 9. The bearing 18 includes an outer ring 18A, balls 18B, an inner ring 18C and a retainer (not shown). The bearing 18 is press-fitted at the outer peripheral surface 18D of the outer ring 18A thereof in the boss 9C of the movable scroll 9. The inner ring 18C has an inner diameter that is larger than the outer diameter of the eccentric pin 16. The bearing 18 is in line contact at the inner peripheral surface 18E of the inner ring 18C thereof with the eccentric pin 16 at the outer peripheral surface 16A thereof. The inner peripheral surface 18E of the inner ring 18C of the bearing 18 is centered on the third axis O3, and the inner ring 18C of the bearing 18 is rotatable on the third axis O3.
The drive shaft 13, the eccentric pin 16 and the bearing 18 cooperate to form a drive mechanism of the compressor for driving the movable scroll 9 relative to the fixed scroll 5. As shown in FIGS. 3 and 4, the third axis O3 is eccentric to the first axis in a first direction (upper direction in the drawings), and the second axis O2 is eccentric to the first and third axes O1 and O3 in a second direction (upper-right direction in the drawings). The eccentric pin 16 revolves around the first axis O1 in a direction where the second axis O2 is located relative to the third axis O3 (clockwise direction in the drawings). The center of gravity C1 of the counterweight 17 is located on an extension of a straight line extending from the third axis O3 to the first axis O1.
As shown in FIG. 1, the scroll wall 5D of the fixed scroll 5 and the scroll wall 9B of the movable scroll 9 are engaged with each other with the distal ends of the scroll walls 5D and 9B in sliding contact with the their associated end plate 9A of the movable scroll 9 and the end plate 5A of the fixed scroll 5, respectively. As shown in FIG. 2, the end plate 9A is formed in the front surface thereof with three or more recesses 10B (only one is shown in the drawings) and a ring 10C is loosely fitted in each recess 10B for receiving therein the distal ends of the respective pins 10A for rolling in contact with the inner peripheral surface of the ring 10C. The recess 10B, the ring 10C and the pin 10A cooperate to form an anti-rotation mechanism of the compressor for preventing the rotation of the movable scroll 9 on its own axis.
The fixed scroll 5 cooperates with the movable scroll 9 to form therebetween a plurality of compression chambers 19. Specifically, each compression chamber 19 is defined by the base 5C, the scroll wall 5D, the end plate 9A and the scroll wall 9B. The end plate 9A cooperates with the shaft support 4 to form therebetween a backpressure chamber 20 that is located on the opposite side of the end plate 9A from the compression chambers 19 and faces the rear end portion of the drive shaft 13. Further, the compressor has a suction region 21 that is defined by the shaft support 4, the side wall 5B of the fixed scroll 5 and the radially outermost portion of the movable scroll 9.
The suction chamber 7 communicates with the suction region 21 through a suction passage 22 that is formed in the lower portion of the front housing 1 In the suction chamber 7, a stator 23 is fixedly mounted on the inner peripheral surface of the front housing 1, and a rotor 24 is secured to the drive shaft 13 at a position radially inward of the stator 23. The rotor 24, the stator 23 and the drive shaft 13 cooperate to form a motor mechanism of the compressor. The drive shaft 13 is rotatable integrally with the rotor 24 when the stator 23 is energized.
The side wall of the front housing 1 has an inlet port 1C formed therethrough. Although not shown in the drawings, the inlet port 1C is connected via a pipe to an evaporator that is further connected to an expansion valve and a condenser via a pipe in a refrigeration circuit of the vehicle air conditioner. In operation of the compressor, low-pressure and low-temperature refrigerant gas in the refrigeration circuit is introduced through the inlet port 1C, the suction chamber 7 and the suction passage 22 into the suction region 21.
The discharge chamber 8 is formed between the base 5C of the fixed scroll 5 and the rear housing 2. The base 5C has a discharge port 5E through which the radially innermost compression chamber 19 is connected to the discharge chamber 8. The discharge port 5E is closed by a discharge valve (not shown), the opening of which is restricted by a retainer 25 mounted to the rear end of the base 5C.
The rear housing 2 is formed with an oil separation chamber 2A that extends vertically behind the discharge chamber 8. The oil separation chamber 2A is separated from the discharge chamber 8 by a partition wall 2B. The partition wall 2B is formed therethrough with a discharge hole 2C through which the oil separation chamber 2A communicates with the discharge chamber 8. In the oil separation chamber 2A, an oil separator 26 is provided for separating lubricating oil contained in refrigerant gas. The oil separator 26 is of a generally cylindrical shape and fitted in the upper portion of the oil separation chamber 2A. Lubricating oil contained in the refrigerant gas introduced from the discharge chamber 8 through the discharge hole 2C into the oil separation chamber 2A is separated from the refrigerant gas by the oil separator 26 under the influence of centrifugal force. The separated oil is dropped into the bottom of the oil separation chamber 2A and stored therein. The part of the oil separation chamber 2A located above the oil separator 26 forms an outlet port 2D of the compressor that is connected through a pipe to the condenser of the refrigeration circuit.
The oil separation chamber 2A and the discharge chamber 8 are connected at the bottom thereof with each other through an oil hole 2E. The discharge chamber 8 is connected to the backpressure chamber 20 through a supply passage 27. The supply passage 27 is provided by a communication hole 27A and a slit 27B. The communication hole 27A extends through the side wall 5B of the fixed scroll 5. The slit 27B is formed through a plate 28 that is interposed between the shaft support 4 and the movable scroll 9. The slit 27B is connected to the communication passage 27A and extends circularly to the backpressure chamber 20. Part of high-pressure refrigerant gas in the discharge chamber 8, which contains lubricating oil, is delivered through the supply passage 27 into the backpressure chamber 20.
In the above-described compressor, when the drive shaft 13 of the motor mechanism is rotated, the eccentric pin 16 is revolved around the first axis O1 in R direction, as shown in FIG. 4. The outer peripheral surface 16A of the eccentric pin 16 slides and rolls on the inner peripheral surface 18E of the inner ring 18C of the bearing 18. The inner ring 18C is rotated on the third axis O3 while revolving around the first axis O1, and the outer ring 18A is revolved around the first axis O1. The pin 10A slides and rolls on the inner peripheral surface of the ring 10C, and the ring 10C slides and rolls on the inner peripheral surface of the recess 10B. As a result, the movable scroll 9 is revolved around the first axis O1. The counterweight 17 serves to cancel the centrifugal force caused by the revolution of the movable scroll 9.
Each compression chamber 19 between the scroll walls 5D and 9B of the fixed and movable scrolls 5 and 9 is moved inwardly while reducing its volume with the revolution of the movable scroll 9. Therefore, refrigerant gas introduced from the evaporator through the inlet port 1C, the suction chamber 7 and the suction passage 22 into the suction region 21 is compressed in the compression chamber 19. Refrigerant gas compressed to a predetermined discharge pressure is discharged through the discharge port 5E into the discharge chamber 8. The refrigerant gas is delivered through the discharge hole 2C into the oil separation chamber 2A where lubricating oil contained in the refrigerant gas is separated. Lubricating oil separated from the refrigerant gas is dropped from the oil separator 26 into the bottom of the oil separation chamber 2A and stored therein. The lubricating oil stored in the oil separation chamber 2A is then delivered along with a small amount of refrigerant gas through the supply passage 27 to the backpressure chamber 20. The refrigerant gas from which the lubricating oil has been separated is delivered through the oil separator 26 and the outlet port 2D into the condenser.
While the drive shaft 13 is being rotated, rotational force F1 acts on the eccentric pin 16, as shown in FIG. 4, contributing to the compression of refrigerant gas in the compression chambers 19. Thus, the eccentric pin 16 receives reaction force F1′ that is directed in opposite direction to the rotational force F1. Driving force F2, which is directed in a direction from the third axis O3 to the second axis O2, acts on the eccentric pin 16. In such a case, pressing force F3, which is the vector difference between the driving force F2 and the rotational force F1, is applied to the bearing 18 from the eccentric pin 16 so as to press the movable scroll 9 to the fixed scroll 5, which improves the sealing between the fixed and movable scrolls 5 and 9. Further, the compressor dispenses with a conventional bush, resulting in the reduction of the number of parts.
Furthermore, no provision of a bush between the eccentric pin 16 and the movable scroll 9 allows the eccentric pin 16 to have a diameter that is large enough to ensure sufficient strength of the eccentric pin 16 in a small-size compressor.
As described above, the compressor according to the present invention allows reduced number of parts, as well as improving the performance of sealing between the fixed and movable scrolls 5 and 9. The compressor also provides an eccentric pin having a sufficient strength in a small-size compressor. Particularly, the drive shaft 13, the eccentric pin 16 and the counterweight 17 are formed integrally in the present embodiment, which is advantageous in reduction of the number of parts of the compressor. This allows reduced weight and size of the compressor and makes it easier to mount the compressor in a vehicle.
Further, no provision of a bush in the compressor increases the distance between the second and third axes O2 and O3 and permits more flexible designing of the compressor and the reduction of the accumulation of tolerance in assembled parts. The eccentric pin 16 can be made with an increased diameter and, therefore, the flexibility of selecting material for the drive shaft 13 is enhanced, which makes it easier to design the compressor and reduces the manufacturing cost of the compressor.
FIG. 5 shows the second embodiment of the present invention. In FIG. 5, same reference numerals are used for the common elements or components in the first and second embodiments, and the description of such elements or components for the second embodiment will be omitted. In the second embodiment, a component 30 including an eccentric pin 30A and a counterweight 30B is provided separately from a drive shaft 29 of the compressor. The component 30 is coupled to the drive shaft 29 by press fitting, so that the eccentric pin 30A and the counterweight 30B are integrated with the drive shaft 29. That is, the eccentric pin 30A and the counterweight 30B are integrally mounted on the drive shaft 29.
According to the second embodiment, scroll compressors of various specifications can be manufactured by increasing the number of kinds of component 30, which minimizes manufacturing cost increase while maintaining versatility of the drive shaft 29. Additionally, the second embodiment offers the advantages similar to those of the first embodiment.
The above embodiments may be modified in various ways as exemplified below.
The bearing 18, which is provided by a roller bearing, may be replaced with a plane bearing.
The present invention may be applied to a pump as well as to a compressor.

Claims

1. A scroll-type fluid machine, comprising:

a fixed scroll and a movable scroll engaged with each other;

an anti-rotation mechanism for preventing the rotation of the movable scroll on its own axis; and

a drive mechanism for driving the movable scroll in orbital motion relative to the fixed scroll, the drive mechanism including:

a drive shaft rotatable on a first axis;

an eccentric pin revolving around the first axis with the rotation of the drive shaft, the eccentric pin having an outer peripheral surface centered on a second axis that is parallel to and eccentric to the first axis; and

a bearing mounted to the movable scroll, the bearing having an inner peripheral surface centered on a third axis that is parallel to and eccentric to the first and second axes, the inner peripheral surface being in contact with the outer peripheral surface of the eccentric pin,

wherein pressing force is applied to the bearing from the eccentric pin due to the arrangement of the first, second and third axes so as to press the movable scroll to the fixed scroll.

2. The scroll-type fluid machine according to claim 1, further comprising a counterweight having center of gravity on an extension of a straight line extending from the third axis to the first axis, the counterweight being formed integrally with the drive shaft and the eccentric pin.

3. The scroll-type fluid machine according to claim 1, further comprising a counterweight having center of gravity on an extension of a straight line extending from the third axis to the first axis, wherein the eccentric pin and the counterweight are integrally mounted on the drive shaft.

4. The scroll-type fluid machine according to claim 2, wherein the movable scroll is formed with a cylindrical boss centered on the third axis, and the bearing is provided by a roller bearing mounted in the boss.

5. The scroll-type fluid machine according to claim 1, wherein rotational force for rotating the movable scroll and driving force directed in a direction from the third axis to the second axis are generated by the rotation of the drive shaft, and the pressing force is the vector difference between the rotational force and the driving force.

6. The scroll-type fluid machine according to claim 5, wherein the scroll-type fluid machine is a compressor, and the rotational force serves to compress refrigerant gas.

7. The scroll-type fluid machine according to claim 1, wherein the bearing includes an inner ring having an inner diameter that is larger than the outer diameter of the eccentric pin, the inner ring being in line contact with the outer peripheral surface of the eccentric pin.