JP2000337273A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To facilitate machining related to an intermediate pressure regulating valve by forming a rotary scroll back face space where pressure becomes intermediate pressure, between the rotary scroll and a frame for supporting it axially, and disposing an intermediate pressure regulating valve for controlling the pressure in the space, radial direction in a right-angled direction to the shaft of the frame. SOLUTION: During the operation of a compressor, a refrigerant is led into a compression chamber 1d between a fixed scroll 1 and a rotary scroll 2 from an intake pipe 10a, and the refrigerant becomes high in pressure due to the volume decrease of the compression chamber 1d consequent to the eccentric turning motion of the rotary scroll 2 driven by a motor 7 and is discharged into a closed container 10 from a discharge port 1f of the fixed scroll 1. At this time, refrigerator oil 10e at the bottom of the closed container 10 is led to a rotary shaft bearing part 2g by differential pressure through a hollow space 4g axially piercing a main shaft 4, and the refrigerator oil 10e fills a boss part space 2h, becoming intermediate pressure due to restricting action in the rotary shaft bearing part 2g and is led to a low pressure space via an intermediate pressure regulating valve 31 and taken into the compression chamber 1g together with low pressure refrigerant gas.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for refrigeration and air conditioning equipment.

[0002]

2. Description of the Related Art FIG. 7 and FIG.
FIG. 7 is a view showing a conventional scroll compressor disclosed in Japanese Patent Application No. 0-330775, FIG. 7 is a longitudinal sectional view of the scroll compressor, and FIG. 8 is an explanatory diagram around an intermediate pressure adjusting valve of the scroll compressor.
In the drawing, reference numeral 1 denotes a fixed scroll, and an outer peripheral portion is fastened to the guide frame 15 by bolts (not shown). Plate-shaped spiral teeth 1b are formed on one surface (the lower side in FIG. 7) of the base plate portion 1a. Fixed scroll 1
The suction pipe 10a is press-fitted through the closed container 10 and the discharge pipe 10b is press-fitted into the closed container 10 on the side surface of the container.

Reference numeral 2 denotes an orbiting scroll, which is provided with plate-shaped spiral teeth 2b having substantially the same shape as the plate-shaped spiral teeth 1b of the fixed scroll 1 on the upper surface of the base plate portion 2a. A compression chamber 1d is formed. Plate-shaped spiral tooth 2 of base plate 2a
A hollow cylindrical boss 2f is formed at the center of the surface on the side opposite to b, and is rotatably engaged with the swing shaft 4b at the upper end of the main shaft 4.

The compliant frame 3 has two upper and lower cylindrical surfaces 3d and 3e provided on an outer peripheral portion thereof, which are radially supported by cylindrical surfaces 15a and 15b provided on an inner peripheral portion of the guide frame 15. Motor 7 in the center
The main bearing 3c and the sub main bearing 3h which support the main shaft 4 rotated and driven in the radial direction are formed.

[0005] In addition, the compliant frame 3
An intermediate pressure regulating valve storage space 3p is also formed, and one end (lower side in FIG. 8) of the intermediate pressure regulating valve storage space 3p communicates with the boss external space 2h via the intermediate pressure regulating valve front passage 3j. At the same time, the other end (upper side in FIG. 8) communicates with the base plate external space 2i via the intermediate pressure regulating valve rear passage 3n.

In the intermediate pressure adjusting valve storage space 3p, an intermediate pressure adjusting valve 31 is reciprocally movable at a lower part thereof, and an intermediate pressure adjusting spring retainer 3t is fixed to the compliant frame 3 at an upper part thereof. It is stored and stored,
The intermediate pressure adjusting valve 3l and the intermediate pressure adjusting intermediate pressure adjusting spring retainer 3t house an intermediate pressure adjusting spring 3m shorter than its natural length.

[0007] The refrigerating machine oil 10e at the bottom of the sealed container 10 is guided to the swing bearing portion 2g through a hollow space 4g penetrating the main shaft 4 in the axial direction by a differential pressure. The refrigerating machine oil 10e, which has become the intermediate pressure by the throttle action of the swing bearing 2g,
A space (boss portion space) 2h surrounded by the orbiting scroll 2 and the compliant frame 3 is filled, and the space 2h and the low-pressure atmosphere space are guided to the low-pressure space via the intermediate pressure regulating valve 31 connecting the low-pressure atmosphere space. The refrigerant gas is sucked into the compression chamber 1d.

During the compression stroke, the refrigerating machine oil 10e is opened together with the high-pressure refrigerant gas from the discharge port 1f into the closed container 10, where it is separated from the refrigerant gas and again closed container 1
Return to the bottom.

The boss space 2h maintains a differential pressure determined by the spring force of the intermediate pressure adjusting spring 3m and the cross-sectional area of the intermediate pressure adjusting valve front flow path 3j. It is set to an intermediate pressure that is higher by the minute. Therefore, the downward force acting on the orbiting scroll 2 is partially canceled by the intermediate pressure, so that the thrust force can be reduced.

[0010]

However, since the intermediate pressure regulating valve 31 is arranged in the axial direction, it is difficult to process the intermediate pressure regulating valve upstream channel 3j and the intermediate pressure regulating valve downstream channel 3n. In addition, since the intermediate pressure adjusting spring retainer 3t faces the thrust bearing 3a side, there is a problem that the thrust bearing 3a is worn or seized due to a reduction in the thrust area.

The present invention has been made in order to solve such a problem, and the intermediate pressure adjusting valve of the scroll compressor is arranged in the radial direction to perform machining only in one direction, thereby greatly reducing the machining cost. The purpose is to do. Another object is to eliminate wear and seizure of the thrust bearing. effective. It is another object of the present invention to eliminate the need for tangential machining of a compliant frame, thereby greatly reducing machining costs.

[0012]

A scroll compressor according to the present invention is provided with a closed container and provided in the closed container.
A fixed scroll and an orbiting scroll in which plate-shaped spiral teeth on a base plate are meshed with each other to form a compression chamber, a compliant frame for supporting the orbiting scroll in the axial direction, and the compliant frame A guide frame that supports the radial direction of the oscillating scroll, an oscillating scroll back space formed between the oscillating scroll and the compliant frame and having an intermediate pressure reduced from the discharge pressure, and a diameter of the compliant frame in a direction perpendicular to the axis. And an intermediate pressure regulating valve arranged in the direction to control the intermediate pressure in the space behind the orbiting scroll.

[0013] Further, a spring for urging the intermediate pressure adjusting valve and a spring retainer for holding the spring are provided.

Further, the spring retainer is partially press-fitted into the inner circumference of the intermediate pressure adjusting valve housing space to secure the flow path of the refrigerant gas.

Further, the spring retainer is press-fitted to the entire periphery of the intermediate pressure adjusting valve storage space, and the spring retainer is provided with an opening serving as a flow path for the refrigerant gas.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. Embodiment 1 FIG. 1 to 4 show the first embodiment. FIG. 1 is a longitudinal sectional view of a scroll compressor, FIG. 2 is a partial longitudinal sectional view of main parts, FIG. 3 is a perspective view of main parts, and FIG. 3 is a partial vertical sectional view of FIG. In the figure, reference numeral 1 denotes a fixed scroll, the outer periphery of which is fastened to the guide frame 15 by bolts (not shown). Plate-shaped spiral teeth 1b are formed on one surface (the lower side in FIG. 1) of the base plate portion 1a, and two Oldham guide grooves 1c are formed substantially in a straight line on the outer peripheral portion. This Oldham guide groove 1
The c is engaged with a claw 9c of the Oldham ring 9 slidably in a reciprocating manner. Further, a suction pipe 10 a through which the suction refrigerant passes is penetrated through the closed casing 10 and pressed into the side surface of the fixed scroll 1.

Reference numeral 2 denotes an orbiting scroll, which is provided with plate-shaped spiral teeth 2b having substantially the same shape as the plate-shaped spiral teeth 1b of the fixed scroll 1 on the upper surface of the base plate portion 2a. A compression chamber 1d is formed. Plate-shaped spiral tooth 2 of base plate 2a
A hollow cylindrical boss 2f is formed at the center of the surface on the side opposite to b, and is rotatably engaged with the swing shaft 4b at the upper end of the main shaft 4.

Further, a thrust surface 2d slidably pressed against the thrust bearing 3a of the compliant frame 3 is formed on the surface of the base plate 2a opposite to the plate-shaped spiral teeth 2b. On the outer peripheral portion of the orbiting scroll base plate 2a, two Oldham guide grooves 2e having a phase difference of 90 degrees with the Oldham guide groove 1c of the fixed scroll 1 are formed substantially in a straight line. The pawl 9a of the Oldham ring 9 is slidably engaged in a reciprocating manner. The base plate 2a
Has an extraction hole 2j passing through the compression chamber 1d and the thrust surface 2d.
Is provided to extract the refrigerant gas during compression and guide it to the thrust surface 2d.

The compliant frame 3 has two upper and lower cylindrical surfaces 3d and 3e provided on the outer peripheral portion thereof, which are radially supported by cylindrical surfaces 15a and 15b provided on the inner peripheral portion of the guide frame 15. Motor 7 in the center
The main bearing 3c and the sub main bearing 3h which support the main shaft 4 rotated and driven in the radial direction are formed. Further, a communication passage 3s is provided which penetrates in the axial direction from within the thrust bearing 3a, and the thrust bearing side opening 2
k is arranged so as to face the orbiting scroll extraction hole 2j.

The opening 2k on the thrust surface side of the extraction hole 2j is
During normal operation, the drawn circular locus is arranged so as to fit in the opening 3f of the communication passage provided inside the bearing surface of the thrust bearing 3a of the compliant frame 3, and the close contact between the orbiting scroll 2 and the compliant frame 3 is achieved. Due to the sliding, there is no leakage to the suction pressure atmosphere space 1g.

The configuration around the intermediate pressure regulating valve and the compliant frame will be described with reference to FIGS. In the figure, 3j is a flow path before the intermediate pressure regulating valve, 3n is a flow path after the intermediate pressure regulating valve, 31 is an intermediate pressure regulating valve, 3m is an intermediate pressure regulating spring,
Reference numeral 3t denotes an intermediate pressure adjusting spring retainer, 3u denotes a spring retainer fixing bolt, and 3w denotes a spring retainer fixing flat portion.

An intermediate pressure adjusting valve 31 and an intermediate pressure adjusting spring 3m are accommodated in an intermediate pressure adjusting valve housing space 3p of the compliant frame 3, and these are held by spring holding fixing bolts 3u via an intermediate pressure adjusting spring holder 3t. It is fixed with. Further, on the compliant frame 3, a spring holding fixing flat portion 3w is formed by tangential machining or the like so that the intermediate pressure adjusting spring holding 3t and the spring holding fixing bolt 3u can be easily attached.

Although the outer peripheral surface 15g of the guide frame 15 is fixed to the closed container 10 by shrink fitting or welding, a notch 15c provided on the outer peripheral portion thereof is provided.
As a result, the high-pressure refrigerant gas discharged from the discharge port 1f of the fixed scroll 1 is supplied to the discharge pipe 10 provided on the motor side.
The flow path leading to b is secured. Guide frame 1
5 has a cylindrical surface 1 engaging with upper and lower cylindrical surfaces 3d and 3e formed on the outer peripheral surface of the compliant frame 3.
5a, 15b and a seal groove for accommodating a seal material
And sealing materials 16a, 16b, respectively.
Is installed.

The frame space 15f formed by the inner peripheral surface of the guide frame 15 and the outer peripheral surface of the compliant frame 3 sealed by using these two sealing materials communicates only with the communication passage 3s of the compliant frame 3. , The refrigerant gas in the middle of compression supplied from the orbiting scroll extraction hole 2j is sealed.

Reference numeral 4 denotes a main shaft, the upper end of which is a swing shaft 4 rotatably engaged with a swing bearing 2c of the swing scroll 2.
The main shaft balancer 4e is shrink-fitted underneath. Furthermore, a main shaft portion 4c rotatably engaged with the main bearing 3c and the sub main bearing 3h of the compliant frame 3 is formed thereunder. A sub shaft 4d rotatably engaged with the sub bearing 6a of the sub frame 6 is formed below the main shaft 4, and a rotor 8 is shrink-fitted between the sub shaft 4d and the main shaft 4c. ing.

An upper balancer 8a is provided on the upper end surface of the rotor 8,
A lower balancer 8b is fixed to the lower end surface, and a static balance and a dynamic balance are obtained by a total of three balancers in addition to the main shaft balancer 4e described above. Further, an oil pipe 4f is press-fitted into the lower end of the main shaft 4 to suck up the refrigerating machine oil 10e accumulated at the bottom of the closed casing 10.

A glass terminal 10f is provided on the side of the closed container 10.
Is installed, and the lead wire from the motor 7 is joined.

Next, the operation will be described. The low-pressure suction refrigerant enters the compression chamber 1d formed by the plate-shaped spiral teeth of the fixed scroll 1 and the orbiting scroll 2 from the suction pipe 10a. The orbiting scroll 2 driven by the motor 7 reduces the volume of the compression chamber 1d together with the eccentric orbiting motion. Due to this compression stroke, the suction refrigerant becomes high pressure and is discharged into the closed container 10 from the discharge port 1f of the fixed scroll 1. During the compression process, the intermediate-pressure refrigerant gas during compression is guided from the extraction hole 2j of the orbiting scroll 2 to the frame space 15f through the communication passage 3s of the compliant frame 3, and maintains the intermediate-pressure atmosphere in this space. . The high-pressure discharge gas fills the closed container 10 with a high-pressure atmosphere,
Eventually, it is discharged from the compressor from the discharge pipe 10b.

The refrigerating machine oil 10e at the bottom of the sealed container 10 is guided to the swing bearing 2g through a hollow space 4g penetrating through the main shaft 4 in the axial direction by a differential pressure. The refrigerating machine oil 10e, which has an intermediate pressure due to the throttling action of the bearing, fills a space (boss space) 2h surrounded by the orbiting scroll 2 and the compliant frame 3, and connects the space with the low-pressure atmosphere space. It is led into the low pressure space via the pressure regulating valve 31 and is sucked into the compression chamber 1d together with the low pressure refrigerant gas. By the compression stroke, the refrigerating machine oil 10e is released into the closed container 10 from the discharge port 1f together with the high-pressure refrigerant gas, separated therefrom and returned to the bottom of the closed container 10 again.

The differential pressure between the cross-sectional area of the intermediate pressure adjusting valve upstream flow path 3j, the pressure in the boss portion space 2h, and the pressure in the base plate external space 2i is smaller than the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m. When the force determined by the product is small, the intermediate pressure regulating valve 31 is closed as shown in FIG. Also, the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m is larger than the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m.
j, the pressure in the boss part space 2h, and the base plate external space 2i
In the case where the force determined by the product of the pressure difference and the pressure difference is large, the intermediate pressure regulating valve 31 opens as shown in FIG. 4 and communicates with the base plate external space 2i via the intermediate pressure regulating valve rear passage 3n. . The post-intermediate-pressure channel 3n is arranged outside the thrust bearing 3a of the compliant frame 3 and may be in communication with the casting surface or by machining.

As described above, the boss space 2h maintains a pressure difference between the pressure in the boss space 2h and the pressure in the outer space 2i of the base plate, which is equal to or less than the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m. Is set to an intermediate pressure higher than the low pressure atmosphere space by this differential pressure. Therefore, the downward force acting on the orbiting scroll 2 is partially canceled by the intermediate pressure, so that the thrust force can be reduced.

The compliant frame 3 has a thrust gas force that causes the fixed scroll 1 and the orbiting scroll 2 to separate in the axial direction by a compressing action, and the compliant frame 3 and the orbiting scroll by an intermediate pressure in the boss space 2h. The sum of the forces that the two are going to separate acts as a downward force in the figure.

On the other hand, the frame space 15f in which the refrigerant gas in the middle of compression is guided to become an intermediate pressure atmosphere acts to separate the compliant frame 3 and the guide frame 15 from each other, and acts on the lower portion exposed to the high pressure atmosphere. The sum of the differential pressures acts as an upward force.

At the time of steady operation, the above-mentioned upward force is set so as to exceed the downward force. Therefore, the compliant frame 3 is guided by the two upper and lower fitted cylindrical surfaces 3d and 3e so as to move upward. Surface. The orbiting scroll 2 slides in close contact with the compliant frame 3 and floats in the same manner, with the plate-shaped spiral teeth 2b contacting the fixed scroll 1 to slide.

Further, at the time of starting or at the time of liquid compression, the above-described thrust gas force becomes large, and the orbiting scroll 2 strongly pushes down the compliant frame 3 via the thrust bearing 3a. A relatively large gap is formed between the tooth tip and the tooth bottom of the fixed scroll 1,
An abnormal pressure rise in the compression chamber is avoided. This operation is called a relief operation, and the generated gap amount is called a relief amount. The relief amount is managed by the distance until the compliant frame 3 and the guide frame 15 collide.

Although part or all of the overturning moment generated in the orbiting scroll 2 is transmitted to the compliant frame 3 via the thrust bearing 3a, the bearing load received from the main bearing 3c and its reaction 2 Since the two resultant forces, that is, the couple generated by the resultant force of the reaction forces received from the upper and lower cylindrical fitting surfaces 3d and 3e of the compliant frame 3 and the guide frame 15 act to cancel the overturning moment, a very good steady state It has the stability of following operation during operation and the stability of relief operation.

According to the above-described embodiment, the intermediate pressure regulating valve front passage 3j is processed in only one direction from the radial direction. For this reason, processing costs can be reduced, and
Since the spring retainer 3t is configured without being disposed on the thrust surface side, problems such as seizure of the thrust bearing 3a due to reduction of the thrust area do not occur.

Embodiment 2 FIG. 5 shows the second embodiment and is a configuration diagram around the intermediate pressure regulating valve. As shown in the drawing, the intermediate pressure adjusting spring retainer 3t is not pressed into the entire circumference, but is, for example, a spring retainer having an octopus-shaped flow path, whereby the spring retainer fixing flat portion shown in the first embodiment is formed. 3w
Is unnecessary, and the flow path can be secured without performing tangential machining on the compliant frame 3.

Embodiment 3 FIG. 6 shows the third embodiment and is a configuration diagram around the intermediate pressure regulating valve. As shown in the drawing, the intermediate pressure adjusting spring retainer 3t is press-fitted all around the circumference and, for example, by providing an opening at the center to secure a flow path, the tangential direction The flow path can be secured without performing machining.

[0040]

In the scroll compressor according to the present invention, the intermediate pressure regulating valve for controlling the intermediate pressure in the space behind the orbiting scroll is disposed in the radial direction in the direction perpendicular to the axis of the compliant frame. Processing is performed, and the cost of machining can be significantly reduced. In addition, since the intermediate pressure control valve can be installed without reducing the area of the thrust bearing, there is an effect of eliminating abrasion and seizure of the thrust bearing.

Further, by providing a spring for biasing the intermediate pressure adjusting valve and a spring retainer for holding the spring,
The boss space can be set to an intermediate pressure with a simple configuration.

Further, since the spring retainer is partially press-fitted into the inner periphery of the intermediate pressure regulating valve housing space to secure the flow path of the refrigerant gas, the compliant frame does not need to be machined in the tangential direction. Thus, the machining cost can be significantly reduced. In addition, since the intermediate pressure control valve can be installed without reducing the area of the thrust bearing, there is an effect of eliminating abrasion and seizure of the thrust bearing.

Further, since the spring retainer is pressed into the entire circumference of the intermediate pressure adjusting valve housing space and the spring retainer is provided with an opening serving as a flow path for the refrigerant gas, the compliant frame does not need to be machined in the tangential direction. Thus, the machining cost can be significantly reduced. In addition, since the intermediate pressure control valve can be installed without reducing the area of the thrust bearing, there is an effect of eliminating abrasion and seizure of the thrust bearing.

[Brief description of the drawings]

FIG. 1 is a view showing a first embodiment and is a longitudinal sectional view of a scroll compressor.

FIG. 2 is a view showing the first embodiment, and is a partial longitudinal sectional view of a main part of the scroll compressor.

FIG. 3 shows the first embodiment, and is a perspective view of main parts of a scroll compressor.

FIG. 4 is a view showing the first embodiment and is a partial vertical sectional view of a main part of the scroll compressor.

FIG. 5 is a view showing the second embodiment, and is a partial longitudinal sectional view of a main part of the scroll compressor.

FIG. 6 shows the third embodiment, and is a partial vertical cross-sectional view of main parts of a scroll compressor.

FIG. 7 is a longitudinal sectional view of a conventional scroll compressor.

FIG. 8 is an explanatory diagram around an intermediate pressure adjusting valve of a conventional scroll compressor.

[Explanation of symbols]

Reference Signs List 1 fixed scroll, 1a base plate portion, 1b plate-shaped spiral tooth, 1c Oldham guide groove, 1d compression chamber, 1f discharge port, 1g suction pressure atmosphere space, 2 oscillating scroll, 2a base plate portion, 2b plate-shaped spiral tooth, 2d thrust surface, 2e Oldham guide groove, 2f boss part, 2g swing bearing space, 2h boss part space, 2i base plate external space,
2j extraction hole, 2k extraction hole thrust surface side opening, 3
Compliant frame, 3a thrust bearing,
3d Upper cylindrical surface, 3e Lower cylindrical surface, 3f Counterbore counterbore, 3g Restrictor, 3j Channel before intermediate pressure regulating valve, 3
1 Intermediate pressure adjusting valve, 3m Intermediate pressure adjusting spring, 3n Intermediate pressure adjusting valve rear passage, 3p Intermediate pressure adjusting valve storage space, 3s communication passage, 3t Intermediate pressure adjusting spring retainer, 3u Spring retainer fixing bolt, 3w spring retainer Flat part for fixing, 4
Main shaft, 4b swing shaft, 4c main shaft, 4d sub bearing, 4e main shaft balancer, 4f oil pipe, 4g
Hollow space, 6 sub-frame, 7 motor, 8 rotor, 8a upper balancer, 8b lower balancer, 9 Oldham ring, 9a swing scroll side claw, 9c fixed scroll side claw, 10 hermetic container, 10a suction pipe, 1
0b discharge pipe, 10d closed container space, 10e refrigerator oil, 10f glass terminal, 15 guide frame,
15a Upper cylindrical surface, 15b Lower cylindrical surface, 15f frame space, 15g outer peripheral surface, 16a Upper seal material, 1
6b Lower sealing material.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Minoru Ishii 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Inventor Takashi Sebata 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Inside Rishi Electric Co., Ltd. (72) Inventor Yasuhiro Suzuki 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Sanbishi Electric Co., Ltd. (72) Inventor Kiyoharu Ikeda 2-3-2 Marunouchi, Chiyoda-ku, Tokyo F-term (Reference) in Denki Co., Ltd.

Claims (4)

[Claims] A fixed scroll and an orbiting scroll provided in the hermetically sealed container, wherein the plate-shaped spiral teeth on the base plate are meshed with each other so as to form a compression chamber; A compliant frame that supports the moving scroll in the axial direction, a guide frame that supports the compliant frame in the radial direction, and an intermediate part formed between the orbiting scroll and the compliant frame and reduced in pressure from the discharge pressure. An orbiting scroll back space that becomes pressure, and an intermediate pressure adjusting valve that is arranged in a radial direction perpendicular to the axis of the compliant frame and controls an intermediate pressure of the orbiting scroll back space. Scroll compressor. 2. The scroll compressor according to claim 1, further comprising: a spring for urging the intermediate pressure adjusting valve, and a spring retainer for holding the spring. 3. The scroll compressor according to claim 2, wherein the spring retainer is partially press-fitted into the inner periphery of the intermediate pressure adjusting valve housing space to secure a flow path of the refrigerant gas. . 4. The scroll compressor according to claim 2, wherein said spring retainer is press-fitted to the entire circumference of the intermediate pressure adjusting valve housing space, and said spring retainer is provided with an opening serving as a flow path for refrigerant gas. Machine.