JP2006342810A - Pressure regulating valve device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pressure regulating valve device requiring a low machining cost and a small number of components. <P>SOLUTION: The pressure regulating valve device comprises a pressure regulating valve device pre-passage, a pressure regulating valve device accommodating space for communicating with the pressure regulating valve device pre-passage, a pressure regulating valve provided in the pressure regulating valve device accommodating space for controlling a communication between the pressure regulating valve device pre-passage for a first pressure and the pressure regulating valve device accommodating space for a second pressure by receiving momentum from a pressure regulating spring, and a pressure regulating spring retainer partially pressed into an inner periphery of the pressure regulating valve device accommodating space for retaining the pressure regulating spring. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a scroll compressor used in a refrigeration air conditioner.

7 and 8 are views showing a conventional scroll compressor in Japanese Patent Application No. 10-330775 filed by the applicant, FIG. 7 is a longitudinal sectional view of the scroll compressor, and FIG. 8 is an intermediate pressure adjustment of the scroll compressor. It is explanatory drawing of the valve periphery.
In the figure, reference numeral 1 denotes a fixed scroll, and an outer peripheral portion is fastened to a guide frame 15 by bolts (not shown). A plate-like spiral tooth 1b is formed on one surface (lower side in FIG. 7) of the base plate portion 1a. A suction pipe 10 a is press-fitted through the sealed container 10 on the side surface of the fixed scroll 1, and a discharge pipe 10 b is press-fitted into the sealed container 10.

  Reference numeral 2 denotes an orbiting scroll. A plate-like spiral tooth 2b having substantially the same shape as the plate-like spiral tooth 1b of the fixed scroll 1 is provided on the upper surface of the base plate portion 2a. Is forming. A hollow cylindrical boss 2f is formed at the center of the surface of the base plate 2a opposite to the plate-like spiral teeth 2b, 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 the outer peripheral portion thereof supported in a radial direction by cylindrical surfaces 15a and 15b provided on the inner peripheral portion of the guide frame 15, and has a central portion. Are formed with a main bearing 3c and a sub main bearing 3h that support the main shaft 4 that is rotationally driven by the motor 7 in the radial direction.

  Further, the compliant frame 3 is also formed with an intermediate pressure adjusting valve storage space 3p, and one end (lower side in FIG. 8) of the intermediate pressure adjusting valve storage space 3p passes through the intermediate pressure adjusting valve front flow path 3j. The other end (upper side in FIG. 8) communicates with the base plate external space 2i via the intermediate pressure regulating valve post-flow passage 3n.

  Further, in this intermediate pressure adjusting valve storage space 3p, an intermediate pressure adjusting valve 3l is fixed to the compliant frame 3 so as to be reciprocally movable in the lower part, and an intermediate pressure adjusting intermediate pressure adjusting spring retainer 3t is fixed to the upper part thereof. The intermediate pressure adjusting spring 3m is accommodated in the intermediate pressure adjusting valve 3l and the intermediate pressure adjusting intermediate pressure adjusting spring retainer 3t by being contracted from the natural length.

  The refrigerating machine oil 10e at the bottom of the hermetic container 10 is guided to the rocking bearing portion 2g through the hollow space 4g penetrating the main shaft 4 in the axial direction by a differential pressure. The refrigerating machine oil 10e having an intermediate pressure due to the squeezing action of the rocking bearing portion 2g fills a space (boss space) 2h surrounded by the rocking scroll 2 and the compliant frame 3, and this space 2h and the low-pressure atmosphere space Is led to the low pressure space via the intermediate pressure regulating valve 3l and is sucked into the compression chamber 1d together with the low pressure refrigerant gas.

  In the compression stroke, the refrigerating machine oil 10e is released into the sealed container 10 from the discharge port 1f together with the high-pressure refrigerant gas, where it is separated from the refrigerant gas and returns to the bottom of the sealed container 10 again.

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 passage 3j, and is higher than the low pressure atmosphere space by this differential pressure. Set to intermediate pressure. For this reason, the downward force acting on the orbiting scroll 2 is partially canceled by this intermediate pressure, and the thrust force can be reduced.
JP-A-11-107938 JP 11-82352 A Japanese Patent Laid-Open No. 61-118580 Japanese Patent Laid-Open No. 1-253581 JP-A-5-187370

  However, since the intermediate pressure adjusting valve 3l is arranged in the axial direction, it is difficult to process the intermediate pressure adjusting valve front passage 3j and the intermediate pressure adjusting valve rear passage 3n, and further, the intermediate pressure adjusting spring presser Since 3t faces the thrust bearing 3a, 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 to solve such a problem, and the intermediate pressure regulating valve of the scroll compressor is arranged in the radial direction so that the machining is performed only in one direction, and the machining cost is greatly reduced. Objective.
It is another object of the present invention to eliminate wear and seizure of thrust bearings.
It is another object of the present invention to eliminate the need for tangential machining on the compliant frame and greatly reduce machining costs.

  A pressure regulating valve device according to the present invention is provided in a pressure regulating valve front passage, a pressure regulating valve storage space communicating with the pressure regulating valve front passage, and a pressure regulating spring provided in the pressure regulating valve housing space. A pressure regulating valve that controls the communication between the first pressure regulating valve front passage and the second pressure regulating valve storage space, and is partially press-fitted into the inner periphery of the pressure regulating valve storage space. And a pressure adjusting spring presser for pressing the pressure adjusting spring.

  With the above-described configuration, the pressure regulating valve device according to the present invention can reduce the processing cost and the number of parts.

Embodiment 1 FIG.
Embodiments of the present invention will be described below with reference to the drawings.
1 to 4 are diagrams showing Embodiment 1, FIG. 1 is a longitudinal sectional view of a scroll compressor, FIG. 2 is a partial longitudinal sectional view of a main portion, FIG. 3 is a perspective view of the main portion, and FIG. FIG.
In the figure, reference numeral 1 denotes a fixed scroll, and an outer peripheral portion thereof is fastened to a guide frame 15 by bolts (not shown). A plate-like spiral tooth 1b is formed on one surface (the lower side in FIG. 1) of the base plate portion 1a, and two Oldham guide grooves 1c are formed on a substantially straight line on the outer peripheral portion. A claw 9c of the Oldham ring 9 is engaged with the Oldham guide groove 1c so as to be slidable back and forth.
Further, a suction pipe 10 a through which the suction refrigerant passes is press-fitted through the sealed container 10 on the side surface of the fixed scroll 1.

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

  Further, a thrust surface 2d that can slide in pressure contact with the thrust bearing 3a of the compliant frame 3 is formed on the surface of the base plate 2a opposite to the plate-like spiral teeth 2b. 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 on the outer peripheral portion of the orbiting scroll base plate 2a on a substantially straight line. Is engaged with a claw 9a of the Oldham ring 9 so as to be slidable back and forth. Further, the base plate 2a is provided with an extraction hole 2j that penetrates the compression chamber 1d and the thrust surface 2d, and has a structure for extracting refrigerant gas that is being compressed and guiding 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 supported in a radial direction by cylindrical surfaces 15a and 15b provided on the inner peripheral portion of the guide frame 15, and has a central portion. Are formed with a main bearing 3c and a sub main bearing 3h that support the main shaft 4 that is rotationally driven by the motor 7 in the radial direction.
Further, a communication passage 3s penetrating in the axial direction from the surface of the thrust bearing 3a is provided, and the thrust bearing side opening 2k is arranged to face the swing scroll extraction hole 2j.

  The thrust surface side opening 2k of the extraction hole 2j is arranged so that a circular locus drawn during normal operation fits in the opening 3f of the communication passage provided in the bearing surface of the thrust bearing 3a of the compliant frame 3, Due to the close sliding of the orbiting scroll 2 and the compliant frame 3, 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 adjustment valve, 3n is a flow path after the intermediate pressure adjustment valve, 3l is an intermediate pressure adjustment valve, 3m is an intermediate pressure adjustment spring, 3t is an intermediate pressure adjustment spring press, and 3u is a spring press fixed. The bolts 3w are flat portions for fixing the spring presser.

The intermediate pressure adjusting valve storage space 3p of the compliant frame 3 stores an intermediate pressure adjusting valve 3l and an intermediate pressure adjusting spring 3m, and these are fixed by a spring press fixing bolt 3u through an intermediate pressure adjusting spring press 3t. ing.
The compliant frame 3 is formed with a spring pressing fixing flat portion 3w by tangential machining or the like so that the intermediate pressure adjusting spring pressing 3t and the spring pressing fixing bolt 3u can be easily attached.

  Although the outer peripheral surface 15g of the guide frame 15 is fixed to the sealed container 10 by shrink fitting or welding, the high pressure discharged from the discharge port 1f of the fixed scroll 1 by the notch 15c provided on the outer peripheral portion. A passage for guiding the refrigerant gas to the discharge pipe 10b provided on the motor side is secured. Further, the inner peripheral surface of the guide frame 15 is provided with two cylindrical grooves 15a and 15b that are engaged with the upper and lower cylindrical surfaces 3d and 3e formed on the outer peripheral surface of the compliant frame 3, and two seal grooves for storing the sealing material. The sealing materials 16a and 16b are respectively 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 with these two sealing materials communicates only with the communication passage 3s of the compliant frame 3, and swings. The refrigerant gas in the middle of compression supplied from the scroll extraction hole 2j is enclosed.

  Reference numeral 4 denotes a main shaft. An upper end portion of the main shaft 4 is formed with a rocking shaft 4b that is rotatably engaged with a rocking bearing 2c of the rocking scroll 2, and a main shaft balancer 4e is fitted on the lower side thereof. Yes. Furthermore, a main shaft portion 4c that is rotatably engaged with the main bearing 3c and the sub main bearing 3h of the compliant frame 3 is formed therebelow. A lower shaft 4d is formed on the lower side of the main shaft 4 so as to be rotatably engaged with the sub-bearing 6a of the sub-frame 6, and the rotor 8 is fitted between the sub-shaft portion 4d and the main shaft 4c. ing.

  An upper balancer 8a is fixed to the upper end surface of the rotor 8 and a lower balancer 8b is fixed to the lower end surface thereof, and a total of three balancers are combined with the main shaft balancer 4e to achieve a static balance and a dynamic balance. . Further, an oil pipe 4f is press-fitted into the lower end of the main shaft 4 so that the refrigerating machine oil 10e accumulated at the bottom of the sealed container 10 is sucked up.

  A glass terminal 10 f is installed on the side surface of the sealed container 10, and a lead wire from the motor 7 is joined thereto.

Next, the operation will be described.
The low-pressure suction refrigerant enters the compression chamber 1d formed by the plate-like spiral teeth of the fixed scroll 1 and the swing scroll 2 from the suction pipe 10a. The orbiting scroll 2 driven by the motor 7 reduces the volume of the compression chamber 1d along with the eccentric turning motion. Due to this compression stroke, the suction refrigerant becomes high pressure and is discharged into the sealed container 10 from the discharge port 1 f of the fixed scroll 1. In the compression stroke, the intermediate-pressure refrigerant gas in the middle of compression is guided to the frame space 15f from the extraction hole 2j of the orbiting scroll 2 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 sealed container 10 with a high-pressure atmosphere, and is eventually discharged from the discharge pipe 10b to the outside of the compressor.

  The refrigerating machine oil 10e at the bottom of the hermetic container 10 is guided to the rocking bearing portion 2g through the hollow space 4g penetrating the main shaft 4 in the axial direction by a differential pressure. The refrigerating machine oil 10e having an intermediate pressure due to the throttle action of the bearing portion fills a space (boss portion space) 2h surrounded by the orbiting scroll 2 and the compliant frame 3, and connects this space and the low-pressure atmosphere space. It is guided to the low pressure space via the pressure regulating valve 3l and sucked into the compression chamber 1d together with the low pressure refrigerant gas. In the compression stroke, the refrigerating machine oil 10e is released into the sealed container 10 from the discharge port 1f together with the high-pressure refrigerant gas, where it is separated from the refrigerant gas and returns to the bottom of the sealed container 10 again.

Rather than the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m, the product of the cross-sectional area of the intermediate pressure adjusting valve front passage 3j, the pressure in the boss portion space 2h, and the pressure in the base plate external space 2i. When the determined force is small, the intermediate pressure regulating valve 3l is closed as shown in FIG.
In addition, the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m is different from the differential pressure between the cross-sectional area of the intermediate pressure adjusting valve front passage 3j, the pressure in the boss portion space 2h, and the pressure in the base plate external space 2i. When the force determined by the product is large, the intermediate pressure regulating valve 3l is opened as shown in FIG. This post-intermediate pressure flow path 3n may be disposed outside the thrust bearing 3a of the compliant frame 3 and communicated with the cast surface or by machining.

  As described above, the boss portion space 2h maintains a differential pressure between the pressure of the boss portion space 2h and the pressure of the base plate outer space 2i that is equal to or less than the spring force determined by the spring constant of the intermediate pressure adjusting spring 3m, The intermediate pressure is set higher than the space by this differential pressure. For this reason, the downward force acting on the orbiting scroll 2 is partially canceled by this intermediate pressure, and the thrust force can be reduced.

  In the compliant frame 3, the compliant frame 3 and the orbiting scroll 2 are separated by the thrust gas force that causes the fixed scroll 1 and the orbiting scroll 2 to be separated in the axial direction by the compression action and the intermediate pressure in the boss space 2h. The sum of the forces to work acts as a downward force in the figure.

  On the other hand, the differential pressure acting on the portion where the frame space 15f, which has led to the refrigerant gas in the middle of compression and becomes an intermediate pressure atmosphere, tries to separate the compliant frame 3 and the guide frame 15 and the portion exposed to the lower high pressure atmosphere. Acts as an upward force.

  During the steady operation, the upward force described above is set to exceed the downward force. For this reason, the compliant frame 3 is guided by the upper and lower two fitted cylindrical surfaces 3d and 3e and floats upward. . The orbiting scroll 2 slides in close contact with the compliant frame 3 and floats in the same manner, and slides with its plate-like spiral teeth 2 b in contact with the fixed scroll 1.

Further, the thrust gas force described above becomes large at the time of start-up or liquid compression, and the orbiting scroll 2 strongly pushes the compliant frame 3 downward through the thrust bearing 3a. A relatively large gap is formed between the tooth tip and the tooth bottom, and an abnormal pressure increase in the compression chamber is avoided. This operation is called a relief operation, and the amount of gap generated 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 two resultant forces that are the reaction thereof, That is, since 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 acts so as to cancel the overturning moment, it follows very good during steady operation. It has operational stability and relief operational stability.

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

  A scroll compressor according to an embodiment of the present invention includes a hermetic container and a fixed scroll provided in the hermetic container and meshed so that plate-like spiral teeth on the base plate form a compression chamber therebetween. And a swing scroll, a compliant frame that supports the swing scroll in the axial direction, a guide frame that supports the compliant frame in the radial direction, and the swing scroll and the compliant frame. An orbiting scroll back space that is an intermediate pressure reduced from the pressure, and an intermediate pressure adjusting valve that is arranged in a radial direction perpendicular to the axis of the compliant frame and controls the intermediate pressure of the orbiting scroll back space. Is.

In the scroll compressor according to the present invention, since the intermediate pressure regulating valve for controlling the intermediate pressure in the back space of the orbiting scroll is arranged in the radial direction of the compliant frame in the direction perpendicular to the axis, machining is performed only in one direction. Costs can be significantly reduced.
Further, since the intermediate pressure control valve can be installed without reducing the area of the thrust bearing, there is an effect of eliminating the thrust bearing wear and seizure accident.

  Further, a spring for biasing the intermediate pressure adjusting valve and a spring presser for pressing the spring are provided.

  In addition, the boss portion space can be set to the intermediate pressure with a simple configuration by providing the spring for biasing the intermediate pressure adjusting valve and the spring presser for pressing the spring.

Embodiment 2. FIG.
FIG. 5 is a diagram showing the second embodiment and is a configuration diagram around the intermediate pressure regulating valve.
As shown in the figure, the spring pressure fixing flat portion shown in the first embodiment is obtained by making the intermediate pressure adjusting spring retainer 3t not a full press fit, for example, by using a spring retainer having a tread foot-shaped channel. 3w becomes unnecessary, and the flow path can be secured without subjecting the compliant frame 3 to tangential machining.

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

In addition, the spring retainer is partially pressed into the inner circumference of the intermediate pressure regulating valve storage space to secure the refrigerant gas flow path, eliminating the need for tangential machining on the compliant frame. Costs can be significantly reduced.
Further, since the intermediate pressure control valve can be installed without reducing the area of the thrust bearing, there is an effect of eliminating the thrust bearing wear and seizure accident.

Embodiment 3 FIG.
FIG. 6 is a diagram showing the third embodiment, and is a configuration diagram around the intermediate pressure regulating valve.
As shown in the figure, the intermediate pressure adjustment spring retainer 3t is press-fitted all around, and for example, by providing an opening in the center and securing a flow path, the compliant frame 3 is tangentially connected to the compliant frame 3 as in the second embodiment. The flow path can be secured without machining.

  Further, a spring presser is press-fitted into the entire circumference of the intermediate pressure regulating valve storage space, and an opening serving as a refrigerant gas flow path is provided in the spring presser.

In addition, the spring retainer is press-fitted all around the intermediate pressure regulating valve storage space, and the spring retainer is provided with an opening that serves as a refrigerant gas flow path, eliminating the need for tangential machining on the compliant frame. Costs can be significantly reduced.
Further, since the intermediate pressure control valve can be installed without reducing the area of the thrust bearing, there is an effect of eliminating the thrust bearing wear and seizure accident.

FIG. 5 is a diagram illustrating the first embodiment, and is a longitudinal sectional view of a scroll compressor. FIG. 2 is a diagram showing the first embodiment and is a partial longitudinal sectional view of a main portion of the scroll compressor. FIG. 5 is a diagram showing the first embodiment, and is a perspective view of main portions of the scroll compressor. FIG. 2 is a diagram showing the first embodiment and is a partial longitudinal sectional view of a main portion of the scroll compressor. It is a figure which shows Embodiment 2, and is a fragmentary longitudinal cross-sectional view of the main location of a scroll compressor. It is a figure which shows Embodiment 3, and is a fragmentary longitudinal cross-sectional view of the main location of a scroll compressor. It is a longitudinal cross-sectional view of the conventional scroll compressor. It is explanatory drawing of the intermediate pressure adjustment valve periphery of the conventional scroll compressor.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Fixed scroll, 1a Base plate part, 1b Plate-shaped spiral tooth, 1c Oldham guide groove, 1d Compression chamber, 1f Discharge port, 1g Suction pressure atmosphere space, 2 Swing scroll, 2a Base plate part, 2b Plate-shaped spiral tooth, 2d Thrust surface, 2e Oldham guide groove, 2f Boss part, 2g Oscillating bearing space, 2h Boss part space, 2i Base plate external space, 2j Extraction hole, 2k Thrust surface side opening of extraction hole, 3 Compliant frame, 3a Thrust bearing, 3d upper cylindrical surface, 3e lower cylindrical surface, 3f connecting passage counterbore, 3g restrictor, 3j intermediate pressure adjusting valve front flow path, 3l intermediate pressure adjusting valve, 3m intermediate pressure adjusting spring, 3n intermediate pressure adjusting valve after 3p intermediate pressure adjusting valve storage space, 3s communication passage, 3t intermediate pressure adjusting spring press, 3u spring press fixing bolt, 3w spring press fixing Carrier section, 4 main shaft, 4b swing shaft section, 4c main shaft section, 4d sub bearing section, 4e main shaft balancer, 4f oil pipe, 4g hollow space, 6 subframe, 7 motor, 8 rotor, 8a upper balancer, 8b lower balancer , 9 Oldham ring, 9a Swing scroll side claw, 9c Fixed scroll side claw, 10 Sealed container, 10a Suction pipe, 10b Discharge pipe, 10d Sealed container inner space, 10e Refrigerating machine oil, 10f Glass terminal, 15 Guide frame, 15a Upper side Cylindrical surface, 15b lower cylindrical surface, 15f frame space, 15g outer peripheral surface, 16a upper sealing material, 16b lower sealing material.

Claims (2)

A flow path before the pressure regulating valve;
A pressure regulating valve storage space communicating with the pressure regulating valve front passage;
Pressure regulation provided in the pressure regulation valve storage space and biased by a pressure regulation spring to control communication between the pressure regulation valve front flow path of the first pressure and the pressure regulation valve storage space of the second pressure A valve,
A pressure adjusting valve device comprising: a pressure adjusting spring press that is partially press-fitted into an inner periphery of the pressure adjusting valve storage space and presses the pressure adjusting spring.   The pressure regulating valve device according to claim 1, wherein the pressure regulating spring presser is formed in a octopus shape.

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