JP2003042087A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem that intermediate pressure can not be maintained stable due to transmission of pressure fluctuation in a compression chamber to a frame space and suction loss is generated due to reverse flow of refrigerant gas in the frame space into the compression chamber in low speed operation to deteriorate stability and performance in a scroll compressor provided with a usual compliant frame in which an extracting hole connecting to the compression chamber and the frame space formed with a guide frame and the compliant frame always communicate with each other. SOLUTION: In the scroll compressor provided with a space of intermediate pressure atmosphere having gas at intermediate pressure in a middle of a compressing process supplied and getting a stationary scroll and a swing scroll into contact, a restricting means is provided in a supply passage supplying gas at intermediate pressure from the compression chamber to the space.

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 / air conditioning equipment.

[0002]

2. Description of the Related Art FIG. 12 is a vertical sectional view of a scroll compressor described in Japanese Patent Application No. 10-330775. In the figure,
Reference numeral 1 is a fixed scroll, and the outer peripheral portion is a guide frame 1.
It is fastened to 5 by a bolt (not shown). Plate-shaped spiral teeth 1b are formed on one surface (lower side in FIG. 12) of the base plate portion 1a, and at the same time, two Oldham guide grooves 1c are formed on the outer peripheral portion in a substantially straight line. The claw 9c of the Oldham ring 9 is reciprocally slidably engaged with the Oldham guide groove 1c. Further, from the side surface of the fixed scroll 1, a suction pipe 10a penetrates the closed container 10 and is press-fitted.

Reference numeral 2 is an orbiting scroll, and plate-like spiral teeth 2b having substantially the same shape as the plate-like spiral teeth 1b of the fixed scroll 1 are provided on the upper surface of the base plate portion 2a, and geometrically. The compression chamber 1d is formed. Plate-shaped spiral teeth 2 of base plate 2a
A hollow cylindrical boss portion 2f is formed in the center of the surface opposite to b, and is rotatably engaged with the swing shaft portion 4b at the upper end of the main shaft 4. Further, on the same surface, a thrust surface 2d is formed which is capable of press-contact sliding with the thrust bearing 3a of the compliant frame 3. On the outer peripheral portion of the orbiting scroll base plate 2a, two Oldham guide grooves 2e having a phase difference of 90 degrees from the Oldham guide groove 1c of the fixed scroll 1 are formed in a substantially straight line. A claw 9a of an Oldham ring 9 is reciprocally slidably engaged therewith. Further, the base plate portion 2a is provided with an extraction hole 2j penetrating the compression chamber 1d and the thrust surface 2d, and has a structure in which a refrigerant gas in the middle of compression is extracted and guided to the thrust surface 2d. It should be noted that the bleed hole 2j is substantially one oblique hole as shown in FIG. 13 (a), or is substantially composed of three holes and the bleed hole plug 2i as shown in FIG. 13 (b). Its function is the same.

The compliant frame 3 has its upper and lower two cylindrical surfaces 3d and 3e radially supported by the cylindrical surfaces 15a and 15b provided on the inner peripheral portion of the guide frame 15, respectively. Motor 7 in the center
A main bearing 3c and a sub-main bearing 3h that radially support the main shaft 4 that is driven to rotate are formed. Further, there is provided a communication passage 3s which axially penetrates the compliant frame 3 from the surface of the thrust bearing 3a and communicates with the frame space 15f, and the thrust bearing side opening 2k thereof is an orbiting scroll extraction hole 2j. Are placed facing each other.

FIG. 14 shows a circular locus during operation of the compliant frame side opening 2k of the extraction hole 2j and the connecting passage 3s.
It is a schematic diagram showing the positional relationship of the swing scroll side opening (concave part) 3f. The compliant frame side opening 2k of the extraction hole 2j has a circular locus formed by the thrust bearing 3a of the compliant frame 3 during normal operation.
It is arranged so as to fit in the opening 3f of the communication passage provided inside the bearing surface of the above, and due to the close sliding of the orbiting scroll 2 and the compliant frame 3, there is no leakage into the suction pressure atmosphere space 1g. ing.

The outer peripheral surface 15g of the guide frame 15 is fixed to the closed container 10 by shrink fitting, welding or the like, but a cutout portion 15c provided on the outer peripheral portion thereof.
The high pressure refrigerant gas discharged from the discharge port 1f of the fixed scroll 1 is discharged by the discharge pipe 10 provided on the motor side.
The flow path leading to b is secured. Also guide frame 1
On the inner peripheral surface of 5, the cylindrical surface 1 that engages with the upper and lower cylindrical surfaces 3d and 3e formed on the outer peripheral surface of the compliant frame 3 is formed.
Sealing grooves 5a and 15b and a sealing material for accommodating the sealing material are provided at two places, and sealing materials 16a and 16b are installed, respectively. 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 and swings. The structure is such that the refrigerant gas in the middle of compression supplied from the scroll bleed hole 2j is enclosed. The base plate portion 1a of the fixed scroll 1 may be fixed to the closed container 10 by shrink fitting, and the guide frame 15 may be fixed thereto by bolting or the like.

Reference numeral 4 denotes a main shaft, the upper end of which is a swing shaft 4 which is rotatably engaged with a swing bearing 2c of the swing scroll 2.
b is formed, and the spindle balancer 4e is shrink-fitted on the lower side thereof. Further, a main shaft portion 4c which is rotatably engaged with the main bearing 3c and the sub-main bearing 3h of the compliant frame 3 is formed therebelow. Further, a sub shaft portion 4d that rotatably engages with the sub bearing 6a of the sub frame 6 is formed on the lower side of the main shaft 4, and the rotor 8 is shrink-fitted between the sub shaft portion 4d and the above-mentioned main shaft portion 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 including the above-described main shaft balancer 4e provide 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 as to suck up the refrigerating machine oil 10e accumulated in the bottom of the closed container 10. A glass terminal 10f is provided on the side surface of the closed container 10.
Is installed and the lead wire from the motor 7 is joined.

Next, the basic operation of this scroll compressor 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 moves in an eccentric orbiting motion together with the compression chamber 1d.
Reduce the volume of. Due to this compression process, the suctioned refrigerant has a high pressure and is discharged into the closed container 10 through the discharge port 1f of the fixed scroll 1. In the compression stroke, the refrigerant gas having an intermediate pressure during the compression is discharged from the extraction hole 2j of the orbiting scroll 2 into the communication passage 3 of the compliant frame 3.
After passing through s, it is guided to the frame space 15f and maintains the intermediate pressure atmosphere in this space. The high-pressure discharge gas fills the closed container 10 with a high-pressure atmosphere, and eventually the discharge pipe 1
It is discharged from the compressor from 0b.

Refrigerating machine oil 10e at the bottom of the closed container 10 is guided to the swing bearing portion 2g by a differential pressure through a hollow space 4g that axially penetrates the main shaft 4. Refrigerating machine oil 10e, which has an intermediate pressure due to the throttling action of the bearing, fills the 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 guided to a low pressure space via a regulating valve (not shown) and is compressed chamber 1d together with a low pressure refrigerant gas.
Inhaled into. Due to the compression process, the refrigerating machine oil 10e is released from the discharge port 1f into the closed container 10 together with the high-pressure refrigerant gas, where it is separated from the refrigerant gas and returns to the bottom of the closed container.

Now, in the compliant frame 3,
The sum of the thrust gas force that causes the fixed scroll 1 and the orbiting scroll 2 to separate axially due to the compression action and the force that causes the compliant frame 3 and the orbiting scroll 2 to separate due to the intermediate pressure in the boss space 2h. , Acts as a downward force in the figure. On the other hand, the total of the force acting on the compliant frame 3 in the frame space 15f, which is in the intermediate pressure atmosphere by guiding the refrigerant gas being compressed, and the differential pressure acting on the lower exposed portion in the high pressure atmosphere, are compliant. It acts as an upward force on the frame 3. The above-mentioned upward force is set to exceed the downward force during steady operation, so that the compliant frame 3 has two upper and lower fitted cylindrical surfaces 3d and 3e.
It is guided by and floats up. The orbiting scroll 2 slides in close contact with the compliant frame 3 and similarly floats, and its plate-like spiral teeth 2b come into contact with the fixed scroll 1 to slide.

Further, the thrust gas force described above increases at the time of start-up or liquid compression, and the orbiting scroll 2 strongly pushes down the compliant frame 3 via the thrust bearing 3a, so that it is fixed to the orbiting scroll 2. A relatively large gap is created between the tooth top and the tooth bottom of the scroll 1, and an abnormal pressure rise 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 some or all of the overturning moment generated in the orbiting scroll 2 is transmitted to the compliant frame 3 via the thrust bearing 3a, it is a bearing load received from the main bearing 3c and its reaction. Two resultant forces, that is, a couple force generated by a resultant force of reaction forces received from the upper and lower two cylindrical fitting surfaces 3d and 3e of the compliant frame 3 and the guide frame 15 act to cancel the overturning moment, and thus a very good steady state is achieved. It has stability of following motion during operation and stability of relief motion.

Here, the frame space 1 for generating the levitation force of the compliant frame 3 and the orbiting scroll 2.
The intermediate pressure of 5f will be supplementarily described. Frame space 1
The intermediate pressure of 5f is supplied with the refrigerant gas being compressed in the compression chamber 1d through the orbiting scroll extraction hole 2j and the compliant frame communication passage 3s. The connection of the refrigerant gas from the extraction hole 2j to the communication passage 3s is as shown in FIG.
It is constituted by a circular locus center of the compliant frame side opening 2k of the bleed hole 2j and a thrust bearing side recess 3f which is concentric therewith and has a large radius.

FIG. 15 is an explanatory diagram of the plate-like spiral tooth 2b side opening (opening opening to the compression chamber side) 2m and the crank angle of the extraction hole arranged in the orbiting scroll 2. The crank angle is 0 degree when the crescent-shaped compression chamber is first formed on the outer peripheral side of the spiral tooth, and then the revolution angle of the orbiting scroll (spindle 4).
Rotation angle), and the crank angle is 90, 180, 27
As the compression chamber volume decreases as the temperature becomes 0 degrees, the compression stroke of the refrigerant gas is performed. The plate-shaped spiral tooth side opening 2m of the extraction hole 2j is set at a position which always faces the crescent-shaped compression chamber 1d geometrically constituted by the plate-shaped spiral teeth 1b, 2b of the fixed scroll 1 and the orbiting scroll 2. Therefore, the intermediate pressure refrigerant gas in the frame space 15f does not flow back into the space 1g of the suction pressure atmosphere through the communication passage 3s and the extraction hole 2j. This is because when the backflow of the refrigerant gas from the frame space 15f to the suction pressure atmosphere space 1g occurs, the volumetric efficiency decreases and the performance of the compressor is impaired. Therefore, the plate-shaped spiral tooth side opening 2m of the extraction hole 2j is arranged relatively to the center of the orbiting scroll plate-shaped spiral tooth 2b. Specifically, from the winding end (outer) position of the orbiting scroll plate-like spiral teeth 2b, at least one or more inner base plate 2a.
14 (in FIG. 14, just one turn inside from the winding end position of the swing scroll plate-shaped spiral tooth 2b).

FIG. 16 shows the crank angle and the pressure in the compression chamber 1d,
It is a view showing the atmosphere of the plate-like spiral tooth side opening 2m of the extraction hole 2j and the pressure transition of the frame space 15f. The crank angle is defined as 0 degree when the crescent-shaped compression chamber 1d formed by the plate-shaped spiral teeth of the fixed scroll and the orbiting scroll is first formed on the outer peripheral side of the spiral tooth, and the plate-shaped spiral tooth of the extraction hole 2j is defined. The side opening 2m was set at a position facing the compression chamber 1d in a section of a crank angle of 0 to 360 degrees. The compression chamber pressure reaches the discharge (high pressure) pressure (Pd) at a crank angle of about 1.25 rotations (360 + 90 degrees) and is discharged from the discharge port 1f. On the other hand, the plate-like spiral tooth side opening 2 of the extraction hole 2j
In the vicinity of m, one compression chamber pressure is opened up to a crank angle of 0 to 360 degrees, but since it opens to one compression chamber outside at 360 degrees, the pressure sharply drops in a discontinuous manner (intake). Pressure Ps). Since the frame space 15f constantly faces the compression chamber 1d via the extraction hole 2j and the communication passage 3s, its pressure changes with a slight pressure pulsation due to the fluctuation of the internal pressure of the compression chamber 1d. The average value of the intermediate pressure in the frame space 15f is the integrated average.

Further, this is the minimum value of the intermediate pressure that can be set in the frame space 15f. In FIG. 15, when the plate-shaped spiral tooth side opening 2m of the extraction hole 2j is further shifted to the winding end side of the plate-shaped spiral tooth, the frame space 15f is moved.
This is because a region is formed which communicates with the suction pressure atmosphere space 1g via the extraction hole 2j, and the refrigerant gas flows backward to cause a decrease in volumetric efficiency.

As described above, the intermediate pressure in the frame space 15f generates a pressing force for floating the compliant frame 3 to bring the fixed scroll 1 and the orbiting scroll 2 into axial contact and sliding. At the design stage, it is an important point to set this intermediate pressure value to the necessary minimum so that sliding loss does not increase due to excessive pressing force. If the pressure in the frame space 15f cannot be reduced below the above-mentioned minimum value, the pressing force must be controlled by adjusting the axial projected area of the frame space 15f composed of two sealing materials.

[0018]

In the scroll compressor described above, in which the compliant frame 3 is movable in the axial direction, the force for levitating the compliant frame 3 and the orbiting scroll 2 is applied to the compression chamber. Refrigerant gas having an intermediate pressure is guided to the frame space 15f and generated from the extraction hole 2j provided so as to be opened. The plate-shaped spiral tooth side opening 2m of the extraction hole 2j must be arranged so as to always face the compression chamber. This is because if the bleed hole 2j is arranged so as to face the suction pressure atmosphere space 1g, the intermediate pressure gas in the frame space 15f will flow back to the suction pressure atmosphere side 1g and the volumetric efficiency will decrease, impairing the performance of the compressor.

Therefore, the intermediate pressure set value of the frame space 15f is at least an integrated average of pressures from the formation of the compression chamber to the crank angle of 360 degrees, but when the axial projection area of the frame space 15f cannot be reduced due to other restrictions. However, there is a problem in that the force for floating the compliant frame 3 and the orbiting scroll 2 becomes excessive, which causes deterioration in performance due to increased friction and deterioration in reliability due to seizure at the tooth tips.

The present invention has been made to solve the above problems. Even if the axial projection area of the frame space 15f cannot be reduced due to other restrictions, the intermediate pressure of the frame space 15f can be lowered by an easy means. The object of the present invention is to provide a scroll compressor which has a degree of freedom that can be set accurately to a desired pressure, and has an optimum pressing force of the tooth top to provide good performance and high reliability.

In the scroll compressor described above in which the compliant frame 3 is movable in the axial direction, since the frame space 15f is always in communication with the compression chamber 1d, the intermediate pressure refrigerant gas in the frame space 15f is used. Is affected by the pressure pulsation of the compression chamber, and the differential pressure causes respiratory loss that travels between the two spaces. What is respiratory loss?
6, the frame space 1 at a crank angle of 360 degrees
Since one of the compression chambers open at 5f moves to the outside and the pressure suddenly drops discontinuously, part of the refrigerant gas returns to the compression chamber 1d due to the difference with the intermediate pressure of the frame space 15f, and the compression stroke of the subsequent compression stroke is reduced. Frame space 15f again with progress
Refrigerant retention occurs due to repeated supply to the compressor, which causes an increase in the electric input of the compressor and a lack of capacity. In the low-speed operation region, this respiratory loss becomes significant, and the pressure in the frame space 15f becomes unstable. Therefore, the axial pressing force of the fixed scroll 1 and the orbiting scroll 2 is not stable, and the performance and reliability are reduced. Cause of.

The present invention has been made to solve the above problems, and suppresses the pressure fluctuation of the compression chamber 1d from propagating to the frame space 15f to easily maintain the intermediate pressure in a stable manner. Also aims to obtain a scroll compressor without performance degradation due to respiratory loss.

Further, the scroll compressor in which the compliant frame described above is movable in the axial direction,
As described above, in order to prevent the intermediate pressure refrigerant gas in the frame space 15f from flowing back into the suction pressure atmosphere space 1g,
The vortex-side opening 2m of the extraction hole 2j must always be set to a position where it opens into the compression chamber. Therefore, the spiral-side opening 2m of the extraction hole 2j is arranged relatively on the center side of the spiral. On the other hand, the thrust surface side opening 2 of the extraction hole 2j
k must be set at a position where the circular locus during operation can be kept within the surface of the thrust bearing 3a to suppress leakage to the boss space 2h and the suction pressure atmosphere space 1g other than the communication passage 3s. In such a case, the bleed hole 2j that connects the two openings 2m and 2k is rarely a vertical drill hole in the base plate, and in most cases, as shown in FIG.
As shown in (b), it is composed of diagonal holes or three holes and the bleed hole plug 2i.

At this time, the spiral side opening 2m of the extraction hole 2j
The closer to the center of the spiral, the larger the machining approach angle of the extraction hole (the angle of the oblique hole), and the machining accuracy and tool life will be impaired. Specifically, the probability of breakage of the tool increases. Further, when the extraction hole is composed of three holes and a bleed hole plug, there is a problem that the processing depth of the lateral hole parallel to the base plate becomes large, which similarly causes a problem in processing accuracy and tool life.

The present invention has been made to solve the above-mentioned problems, and the plate-like spiral tooth side opening 2m of the extraction hole 2j is formed.
Is arranged relatively to the outer circumference of the spiral, and the suction pressure atmosphere 1
Even when it approaches g, a scroll compressor is obtained in which the refrigerant gas in the frame space 15f does not flow back into the suction pressure atmosphere space 1g and the volume efficiency is not lowered, and the processing accuracy of the extraction holes 2j and the tool life are not impaired. The purpose is to

[0026]

According to a first aspect of the present invention, there is provided a scroll compressor, which is provided in an airtight container and is fixed in such a manner that plate-like spiral teeth on respective base plates are engaged with each other to form a compression chamber therebetween. A scroll and an orbiting scroll, a main shaft for driving the orbiting scroll, a frame for supporting the main shaft in a radial direction and a for axially supporting the orbiting scroll, and compression of the compression chamber. A scroll compressor provided with a space of an intermediate pressure atmosphere for causing the fixed scroll and the orbiting scroll to come into contact with each other and slide by being supplied with an intermediate pressure gas in the middle of the compression chamber. The supply passage for supplying the intermediate-pressure gas to the space of the intermediate-pressure atmosphere is provided with throttling means.

According to a second aspect of the present invention, there is provided the scroll compressor having the space of the intermediate pressure atmosphere between the orbiting scroll and the frame.

A scroll compressor according to a third aspect of the present invention includes a fixed scroll and an orbiting scroll which are provided in a closed container and in which plate-like spiral teeth on respective base plates are meshed so as to form a compression chamber therebetween. A main shaft for driving the oscillating scroll, a compliant frame for supporting the main shaft in the radial direction and for axially supporting the oscillating scroll, and a radial support for the compliant frame. And a guide frame for controlling the compression chamber to supply a gas at an intermediate pressure during compression of the compression chamber to a frame space provided between the compliant frame and the guide frame. The supply passage for supplying the intermediate-pressure gas during the compression to the frame space is provided with throttling means.

According to a fourth aspect of the present invention, there is provided a scroll compressor having a base plate of the orbiting scroll, one end of which is opened to the compression chamber and the other end of which is opened toward the compliant frame, and the compliant frame. Provided on the frame,
The supply passage is constituted by a communication passage having one end opened to the orbiting scroll side and the other end opened to the frame space, and a throttle means is provided in at least one of the bleed hole or the communication passage. It is a thing.

According to a fifth aspect of the scroll compressor, the throttle means is constituted by another member such as a set bolt with a small hole or a sheet metal with a small hole.

According to a sixth aspect of the present invention, in the scroll compressor, the throttle means is set to have an inner diameter of 0.5 mm or more and 1.0 mm or less.

[0032]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment A first embodiment of the present invention will be described with reference to FIGS. 1 is a vertical cross-sectional view of Embodiment 1 of the present invention. About each part, the same thing as FIG. 12 is attached | subjected the same code | symbol, and abbreviate | omits description. FIG. 2 is a partial cross-sectional view showing the extraction hole 2j and the compliant frame 3 and its periphery, which is a feature of the present invention. In FIGS. 1 and 2, reference numeral 2j is an extraction hole provided in the orbiting scroll base plate 2a. The bleed hole 2j is formed by making a diagonal hole with a small-diameter hole, and is itself a throttle flow passage which is one throttle means. One of the openings of the bleed hole (the opening to the compression chamber) faces the crescent-shaped compression chamber that is geometrically configured with the plate-like spiral teeth of the fixed scroll 1, and the other 2k (the compliant frame). The opening (opening to the side) is arranged in the thrust bearing surface 3a of the compliant frame so that all of its circular locus is fitted.

The connection between the two openings 2m and 2k is shown in FIG.
Although it is configured with small-diameter diagonal holes as shown in Fig. 13, when it is configured with three holes and the bleed hole plug 2i as shown in Fig. 13 (b), the two openings 2m, 2k are respectively By forming a vertical small-diameter drill hole which is a diaphragm means in the plate 2a, a larger diaphragm effect can be obtained.

3 is a compliant frame, and 2
It is supported in the radial direction by engaging the three cylindrical surfaces 3d and 3e with the guide frame 15. Thrust bearing surface 3
A communication passage 3s communicating with the frame space 15f is provided in a, and a recessed portion 3f which is an opening opening to the swing scroll side is formed on the thrust bearing side thereof by circular machining. In the middle of the communication passage 3s, there is provided a throttle flow passage 3g which is a throttle means using a small-diameter drill hole. The recessed portion 3f is provided at a position facing the compliant frame side opening 2k of the orbiting scroll extraction hole 2j,
The center of the circular locus formed by the center and the opening 2k of the bleed hole is arranged offset.

FIG. 3 is a diagram for explaining the intermittent communication means of the first embodiment, in which the circular locus formed by the compliant frame side opening 2k of the orbiting scroll extraction hole 2j during operation and the compliant frame. FIG. 3 is a schematic diagram showing interference of a recessed portion 3f which is a swing scroll side opening of the communication passage 3s. The figure shows a case in which the offset amount and direction are set so that the timing at which the extraction hole 2j and the communication passage 3s communicate with each other is about a half of one revolution of the main shaft 4. Compliant frame side opening 2 of bleed hole 2j
In the section where the circular locus of k deviates from the recessed portion 3f, the compliant frame side opening 2k of the bleed hole is in close contact with the thrust bearing 3a, and the communication between the compression chamber 1d and the frame space 15f is cut off. For the following description, a case in which the opening 2k of the bleed hole and the recess 3f are set as follows is given as an example of the intermittent communication means. As described above, when the crescent-shaped compression chamber is formed for the first time, the crank angle is 0 degree, and the plate-shaped spiral tooth side opening (opening to the compression chamber) 2m of the extraction hole 2j is 0 degree to 3 degrees.
It faces the compression chamber in the section up to 60 degrees. Bleed hole compliant frame side opening 2k
Circular locus center and circular recess 3f at the entrance of connecting passage 3s
With respect to the center, the offset amount and direction are set so that the opening 2k and the recessed portion 3f communicate with each other in the range of 0 to 180 degrees at the crank angle described above.

FIG. 4 shows the crank angle, the compression chamber 1d, the atmosphere of the plate-shaped spiral tooth side opening 2m of the extraction hole 2j and the pressure fluctuation of the frame space 15f in the above setting. The pressure in the compression chamber rises with the compression stroke, reaches a high pressure (discharge pressure Pd) at a crank angle of about 1.25 rotations (360 + 90 degrees), and is discharged from the discharge port 1f. The pressure of the atmosphere of the plate-like spiral tooth side opening 2m of the extraction hole rises with the pressure in the compression chamber, and becomes equal to the pressure in the compression chamber (suction pressure Ps) at the crank angle of 360 ° again at the crank angle of 360 °. fluctuate. On the other hand, in the frame space 15f, the communication between the compression chamber 1d and the frame space 15f is controlled by the intermittent communication means by the extraction hole 2j and the recessed portion 3f to be a crank angle of 0 to 180 degrees in which the pressure fluctuation is relatively small. In addition, the throttling effect of the throttling means of the extraction hole 2j itself and the effect of the throttling channel 3g, which is the throttling means installed in the communication passage 3s, are combined, and the pressure pulsation of the frame space 15f is small, and the pressure fluctuation of the conventional example (FIG. 16) More stable than that. In the section of the crank angle of 180 to 360 degrees where the compression rising gradient becomes large, the recessed portion 3
Since the communication between the compression chamber 1d and the frame space 15f is blocked by the intermittent communication means by f, the pressure fluctuation of the compression chamber 1d does not affect the frame space 15f, and there is no deterioration in performance due to respiratory loss. In particular, the above effect is remarkable in low-speed operation, and the frame space 15f can maintain good reliability and performance due to the stable intermediate pressure.

In FIG. 4, the crank angle of 0 to 180 degrees is set in the communication range between the compression chamber 1d and the frame space 15f.
The pressure value to be extracted can be freely set by adjusting the offset amount and the direction of the recessed portion 3f, and can be set to a value smaller than the minimum value of the intermediate pressure setting of the conventional example. Further, even if the axial projected area of the frame space 15f cannot be adjusted due to other restrictions, an arbitrary intermediate pressure can be easily set in the frame space 15f, so that the compliant frame 3 and the orbiting scroll 2 are also lifted. It is possible to easily obtain the optimum value.

In FIG. 3, the recessed portion 3f of the compliant frame is machined into a circular shape. However, if the offset amount between the center of the circular locus of the compliant frame side opening 2k of the extraction hole and the center of the circular recessed portion 3f is small. In some cases, the sealing distance at the time of disconnecting communication in intermittent communication may not be sufficient. FIG. 5A is a schematic diagram showing this, but especially in a small-sized scroll compressor, the orbiting radius of the opening 2k also becomes small, and the absolute value of this sealing distance must be small. If the seal distance is short, there is a risk of leakage even when shut off. In such a case, the recess 3f
5c does not have a circular shape, but has an irregular recess 3f as shown in FIG. 5 (b).
The seal distance can be increased by molding with an end mill or the like. If forming with a small-diameter end mill causes problems in tool life and processing time, the same effect can be obtained by forming by electroforming such as die forming or electric discharge machining. 5 (c) and FIG.
Although (d) shows other examples of the shape of the recessed portion, various shapes and processing means can be mentioned depending on the required intermediate pressure and the width of the communication section. FIG. 5 is an explanatory view different from FIG. 3 for explaining the intermittent communication means.

Embodiment 2 FIG. 6 illustrates the arrangement of the plate-like spiral tooth side opening 2m of the orbiting scroll extraction hole 2j in Embodiment 2 of the invention, and FIG. 7 illustrates the intermittent communication means of Embodiment 2. It is a figure, and is explanatory drawing about the intermittent communication area | region by the circular locus | trajectory of the compliant frame side opening part 2k of an extraction hole, and the recessed part 3f interference.

The plate-shaped spiral tooth side opening 2m of the orbiting scroll bleed hole 2j shifts further outward than the position shown in FIG. 3 and is installed on the base plate 2a at a position halfway inside from the spiral end position. I am doing it. With this arrangement, the plate-shaped spiral tooth side opening 2m of the extraction hole has a region facing the suction pressure atmosphere space 1g before the compression chamber is formed during one rotation of the main shaft 4. In FIG. 6, the opening 2m faces the suction pressure space 1g in the crank angle range of 180 to 360 degrees, and in the scroll compressor shown in the conventional example, the frame space 1 at this timing.
As described above, the backflow of the refrigerant gas occurs from 5f to the suction pressure atmosphere space 1g, and the volumetric efficiency decreases.

However, in the intermittent communication means according to the second embodiment of the invention, as shown in FIG. 7, the plate-like spiral tooth side opening 2m of the extraction hole faces the suction pressure atmosphere space 1g at a crank angle of 180 to 360 degrees. In the section, the offset amount and the direction of the recess 3f are set so that the compliant frame side opening 2k of the extraction hole 2j does not communicate with the frame space 15f. The refrigerant gas does not flow back into the suction pressure atmosphere space 1g.

FIG. 8 shows the crank angle and the extraction hole 2j in this case.
Plate-like spiral tooth side opening 2m atmosphere, frame space 15f
Shows the pressure fluctuation. The plate-shaped spiral tooth side opening 2m of the extraction hole 2j faces the suction pressure atmosphere in the section of the crank angle of 180 to 360 degrees, and has the suction pressure (Ps). However, as described above, the communication with the frame space 15f is avoided in this section due to the interference between the compliant frame side opening 2k of the extraction hole and the recess 3f.
Therefore, it can be seen that the pressure in the frame space 15f changes in a stable state with little pressure fluctuation as in the case of the first embodiment of the invention. Similarly, since the throttling flow path which is the throttling means of the communication passage 3S described in the first embodiment of the invention is also installed, the intermediate pressure of the frame space 15f can be stably maintained, the respiratory loss in the low speed operation is small, and the good reliability is obtained. Sex and performance can be maintained.

Not only that, the plate-shaped spiral tooth side opening 2m of the extraction hole can be arranged on the relatively outer periphery of the spiral, so that FIG.
As shown in FIG. 7, the machining entrance angle θ1 of the oblique hole of the extraction hole 2j can be made smaller than the machining entrance angle θ2 arranged on the inner circumference, and the machining of the extraction hole with excellent machining accuracy and excellent productivity can be realized. . The tool life can be improved. When the extraction holes 2j are provided in the three holes and the extraction hole plug as shown in FIG. 9B, the processing depth D1 of the horizontal hole parallel to the base plate is equal to the processing depth D2 of the horizontal hole in the inner circumference. It will be smaller compared to
Similarly, it is possible to realize the processing of the extraction hole 2j with high accuracy and high productivity. The tool life can be improved. Further, in the bleed hole 2j having such a configuration, since two small-diameter drill holes, which are throttle means, can be provided through the lateral holes parallel to the base plate 2a,
The throttling effect of the extraction hole 2j is further increased, and the effect of alleviating the pressure fluctuation is also increased, as in the first embodiment of the invention.

Embodiment 3 FIG. 10 (a) shows an example in which a throttle bolt 3g, which is a throttle means in the communication passage 3s of the compliant frame 3, is replaced by a set bolt having a small hole. See also FIG.
In (b), a sheet metal piece having a small hole 3g is installed instead of the set bolt to obtain the same drawing effect. The effect of mitigating the propagation of pressure fluctuations in the compression chamber 1d and the frame space 15f and becoming a resistance against the reverse flow of the refrigerant gas from the frame space 15f to the compression chamber 1d is the same as in the first and second embodiments.

Providing the throttle passage 3g directly in the communication passage 3s as shown in FIGS. 1 and 2 is effective from the viewpoint of reducing the number of parts, but on the other hand, it complicates the machining process and reduces the number of tools required for the machining machine. There are also problems such as an increase. Therefore, it can be said that it is more efficient in terms of productivity to configure a part such as the throttle channel as a separate part and install it separately.

Fourth Embodiment FIG. 11 shows a state of pressure fluctuation propagating to the frame space 15f with the small hole diameter of the extraction hole 2j of the orbiting scroll and the throttle passage 3g of the communication passage 3s of the compliant frame 3 as a parameter. It is a thing. In order to make it easier to see the effect of the throttle, the frame in the case where the compression chamber 1d and the frame space 15f in FIG. 11 are set to communicate with each other within a range of 180 to 360 degrees at a crank angle with a relatively large pressure variation by intermittent communication means The pressure fluctuation in the space 15f is shown.

FIG. 11 shows that the smaller the small hole diameter, the smaller the damping effect of the pressure fluctuation due to the restriction and the larger the pressure fluctuation in the frame space 15f. Further, the smaller the diameter of the small hole, the greater the damping effect of the fluctuating pressure, and the stable intermediate pressure of the frame space 15f can be maintained. However, machining the small hole having an excessively small diameter increases the probability of breakage of the tool and machining. It is not always efficient in terms of speed control.

The small hole diameter of the throttle channel 3g according to the present invention is φ
If it is 1.0 mm or more, the damping effect of the pressure fluctuation is small, and the performance is remarkably reduced due to the respiratory loss in the low speed operation range. In addition, φ0.
If it is less than 5 mm, problems such as an increase in tool breakage probability in drilling a hole and a complicated machining process occur. Taking these into consideration, the small hole diameter of the throttle channel is φ0.5 mm or more and φ1.0 mm.
The following ranges are suitable.

Embodiment 5 In the intermittent communication means, the shorter the communicating section is, the more the damping of the pressure pulsation propagating from the compression chamber 1d to the frame space 15f during normal operation can be obtained, and a stable intermediate pressure can be obtained. However, on the other hand, shortening the communication section may adversely affect the startability of the compressor.

At the time of starting the compressor, the inside of the closed container 10 is balanced at the same pressure. When the compressor starts, the compression chamber 1d
By the compression stroke in (1), an intermediate pressure for floating the orbiting scroll 2 and the compliant frame 3 is generated and starts to be supplied to the frame space 15f. When the communication section between the compression chamber 1d and the frame space 15f is set to be extremely short by the intermittent communication means, the intermediate pressure of the compression chamber 1d is not sufficiently supplied to the frame space 15f and the orbiting scroll 2 and the compliant frame 3 are floated. It is easy for the situation where the force to generate is not generated. In such a case, the time required for the compressor to perform stable operation becomes long, which causes a loss of startability.

In order to obtain good startability, the communication section between the compression chamber 1d and the frame space 15f needs to be at least about 1/4 of one revolution of the crankshaft. In addition, it suppresses pressure propagation from the compression chamber 1d to the frame space 15f during stable operation,
In order to minimize the performance deterioration due to respiratory loss in low speed operation, the communication section between the compression chamber and the frame space must be about 3/4 or less of one revolution of the main shaft 4. Therefore, the compression chamber 1d and the frame space 1 in the intermittent communication means
The communication section of 5f is 1/4 or more during one rotation of the main shaft 4 and 3 /
4 or less is suitable.

The range of the crank angle from which the intermediate pressure is extracted depends on the projected area of the frame space 15f in the axial direction, the force required to levitate the compliant frame 3 and the orbiting scroll 2 pressed against the fixed scroll 1. Since it can be set freely according to the force required for the above, by adjusting the crank angle range of the intermittent communication and the throttle channel diameter described above, as well as the axial projected area of the frame space 15f, the most balanced range in the entire operating range of the compressor can be obtained. It is possible to easily set good specifications.

In the first to fifth embodiments of the present invention, the hermetic compressor mainly used in the small and medium-sized refrigerating and air conditioning systems has been described as an example, but it is adopted in the air conditioning system for automobiles. The same effect can be obtained in a compressor of the type having the drive element on the outside of the compression mechanism housing.

[0054]

In the scroll compressor according to the first aspect of the present invention, the scroll compressor provided in the hermetically sealed container, and the plate-like spiral teeth on the respective base plates are engaged with each other to form a compression chamber therebetween. A scroll and an orbiting scroll, a spindle for driving the orbiting scroll, a frame for supporting the spindle in the radial direction, and a frame for axially supporting the orbiting scroll.
And a space of an intermediate pressure atmosphere for sliding the fixed scroll and the orbiting scroll in contact with each other by supplying an intermediate pressure gas during compression in the compression chamber. In the compressor, since the supply passage for supplying the intermediate pressure gas from the compression chamber to the space of the intermediate pressure atmosphere is provided with the throttling means, the pressure fluctuation of the compression chamber can be prevented from propagating to the space of the intermediate pressure atmosphere. .

In the scroll compressor according to the second aspect of the present invention, since the space of the intermediate pressure atmosphere is provided between the orbiting scroll and the frame, the pressure fluctuation of the compression chamber is the space of the intermediate pressure atmosphere. It is possible to mitigate the propagation to the air conditioner, and performance deterioration due to respiratory loss does not occur even in the low speed operation region.

Further, in the scroll compressor according to the third aspect of the present invention, the fixed scroll provided in the closed container and in which the plate-like spiral teeth on the respective base plates are meshed so as to form a compression chamber therebetween. And an orbiting scroll, a main shaft for driving the orbiting scroll, a compliant frame for supporting the main shaft in a radial direction and for axially supporting the orbiting scroll, and the compliant frame. And a guide frame for supporting in a radial direction, and a scroll compressor for supplying an intermediate pressure gas during compression of the compression chamber to a frame space provided between the compliant frame and the guide frame. In the above, since the supply passage for supplying the intermediate-pressure gas in the middle of compression of the compression chamber to the frame space is provided with the throttling means, the pressure fluctuation of the compression chamber causes Can be relaxed to propagate between, also becomes the resistance of the refrigerant gas flowing back to the compression chamber from the frame space in low-speed operation, it is possible to stably maintain the intermediate pressure of the frame space.

In the scroll compressor according to claim 4 of the present invention, the scroll compressor is provided on the base plate of the orbiting scroll,
An extraction hole having one end opening to the compression chamber and the other end opening to the compliant frame side and the compliant frame, one end opening to the orbiting scroll side, and the other end to the frame space. Since the supply passage is constituted by an open communication passage and at least one of the bleed hole or the communication passage is provided with a throttle means, it is possible to reduce the pressure fluctuation of the compression chamber from propagating to the frame space. Even during low-speed operation, the resistance of the refrigerant gas flowing back from the frame space to the compression chamber becomes a resistance, and the intermediate pressure in the frame space can be stably maintained.

Further, in the scroll compressor according to the fifth aspect of the present invention, since the throttle means is constituted by another member such as a set bolt with a small hole or a sheet metal with a small hole, an orbiting scroll or A complicated compressor hole can be omitted from the compliant frame, and a highly productive scroll compressor can be obtained.

Further, in the scroll compressor according to the sixth aspect of the present invention, since the throttle means is set within the range of the inner diameter φ0.5 mm or more and φ1.0 mm or less, the flow between the compression chamber and the frame space. It is possible to obtain the throttling means excellent in workability while maintaining the road resistance and stably maintaining the intermediate pressure in the frame space.

[Brief description of drawings]

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

FIG. 2 is a partial vertical cross-sectional view of main parts of the scroll compressor according to the first embodiment of the present invention.

FIG. 3 is an explanatory diagram of intermittent communication means of the scroll compressor according to the first embodiment of the present invention.

FIG. 4 is an explanatory diagram of a crank angle and a pressure variation in a frame space of the scroll compressor according to the first embodiment of the present invention.

FIG. 5 is an explanatory diagram of another intermittent communication means of the scroll compressor according to the first embodiment of the present invention.

FIG. 6 is an explanatory diagram of a bleed hole position and a crank angle of the scroll compressor according to the second embodiment of the present invention.

FIG. 7 is an explanatory diagram of intermittent communication means of the scroll compressor according to the second embodiment of the present invention.

FIG. 8 is an explanatory diagram of a crank angle and a pressure variation in a frame space of the scroll compressor according to the second embodiment of the present invention.

FIG. 9 is a layout view of extraction holes of the scroll compressor according to the second embodiment of the present invention.

FIG. 10 is an explanatory view of a throttle means of a communication passage of the scroll compressor according to the third embodiment of the present invention.

FIG. 11 is a frame space pressure fluctuation diagram depending on a crank angle and a throttle channel diameter of a scroll compressor according to a fourth embodiment of the present invention.

FIG. 12 is a vertical cross-sectional view of a conventional scroll compressor.

FIG. 13 is an explanatory diagram of extraction holes of a conventional scroll compressor.

FIG. 14 is an explanatory diagram of a communication portion of a conventional scroll compressor.

FIG. 15 is an explanatory diagram of a bleed hole and a crank angle of a conventional scroll compressor.

FIG. 16 is an explanatory diagram of a crank angle and a pressure variation in a frame space of a conventional scroll compressor.

[Explanation of symbols]

1 fixed scroll, 1a fixed scroll base plate, 1
b Fixed scroll plate spiral tooth, 1d compression chamber, 1g
Intake pressure atmosphere space, 2 orbiting scrolls, 2a
Oscillating scroll base plate, 2b Oscillating scroll plate spiral teeth, 2j bleed hole, 2k bleed hole compliant frame side opening, 2m bleed hole compression chamber opening,
3 compliant frame, 3f connecting passage swing scroll side opening, 3s connecting passage, 4 spindle,
10 airtight container, 15 guide frame, 15f frame space, 17 set bolt with small holes, 18 sheet metal with small holes.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Takeshi Fushiki             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Takashi Sebata             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Yasuki Suzuki             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Minoru Ishii             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. F-term (reference) 3H029 AA02 AA14 AB03 BB43 BB53                       CC05 CC06 CC15 CC25 CC54                       CC87                 3H039 AA03 AA06 AA12 BB22 BB28                       CC08 CC29 CC40

Claims (6)

[Claims] 1. A fixed scroll and an orbiting scroll which are provided in a hermetically sealed container and meshed with each other so that plate-like spiral teeth on respective base plates form a compression chamber therebetween, and the orbiting scroll. A main shaft for driving the main shaft, a frame for supporting the main shaft in the radial direction, and a frame for supporting the oscillating scroll in the axial direction, and a gas at an intermediate pressure during the compression of the compression chamber to supply the fixed scroll. And a space of an intermediate pressure atmosphere for contacting and sliding the orbiting scroll,
A scroll compressor comprising: a scroll compressor, wherein a supply means for supplying a medium pressure gas from the compression chamber to the medium pressure atmosphere space is provided with throttling means. 2. The scroll compressor according to claim 1, wherein a space of the intermediate pressure atmosphere is provided between the orbiting scroll and the frame. 3. A fixed scroll and an orbiting scroll which are provided in a hermetically sealed container and are meshed with each other so that plate-like spiral teeth on respective base plates form a compression chamber therebetween, and the orbiting scroll. A main shaft for driving the main shaft, a compliant frame supporting the main shaft in the radial direction and supporting the swing scroll in the axial direction, and a guide frame supporting the compliant frame in the radial direction. ,
In a scroll compressor for supplying a medium-pressure gas during the compression of the compression chamber to a frame space provided between the compliant frame and the guide frame,
A scroll compressor, characterized in that a throttle means is provided in a supply passage for supplying an intermediate pressure gas in the compression chamber to the frame space. 4. A base plate of the orbiting scroll is provided,
An extraction hole having one end opening to the compression chamber and the other end opening to the compliant frame side and the compliant frame, one end opening to the orbiting scroll side, and the other end to the frame space. The scroll compressor according to claim 3, wherein the supply passage is constituted by an open communication passage, and throttle means is provided in at least one of the extraction hole or the communication passage. 5. The squeezing means is constituted by a separate member such as a set bolt with a small hole or a sheet metal with a small hole, and the like. Scroll compressor. 6. The scroll compressor according to claim 1, wherein the throttle means is set to have an inner diameter of 0.5 mm or more and 1.0 mm or less.