JP5295140B2 - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a spring from protruding from a valve passage against a reverse flow of a refrigerant occurring at operation stop of a compressor and at negative-phase operation. <P>SOLUTION: The valve passage 1f is provided in compression mechanism sections 1, 2, 3, 15 to communicate with an intake pipe 10a provided through a sealed container 10 and with a compression chamber communication passage 1k communicating with a compression chamber 1d. A first valve passage opening part 1j and a second valve passage opening part 1m are provided on both side faces of the valve passage to communicate with the compression chamber communication passage. The first valve passage opening part 1j on a compression chamber communication passage side is formed smaller than the second valve passage opening part 1m on the opposite side to the compression chamber communication passage. A wall 1l for preventing protrusion of the spring is provided on the side face of the valve passage at a position between the first valve passage opening part and a valve stop face 1g. A valve passage upper communication passage 1n bypassing the valve passage is provided in communication with the second valve passage opening part and the first valve passage opening part. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a compressor used in a refrigeration air conditioner, and more particularly to an improvement in a valve passage opening for introducing a refrigerant to be compressed by a scroll compressor from the outside.

  A conventional scroll compressor includes a fixed scroll and a swing scroll having a plate-like spiral tooth in a hermetic container, and the compression scroll chamber is formed by meshing the plate-like spiral tooth of the fixed scroll and the plate-like spiral tooth of the swing scroll. It is formed and compresses the refrigerant in the compression chamber by rotating the swing scroll so as not to rotate with respect to the fixed scroll. A plate-like spiral tooth of the fixed scroll is provided with a valve passage extending in the horizontal direction so as to communicate with the suction pipe, and a valve is slidably provided therein, and the suction pipe passes through the sealed container. It is press-fitted. Further, the valve is urged by the spring in the closing direction of the suction pipe, hits the end face of the suction pipe and is sealed at the end face to prevent the refrigerant from flowing back to the outside of the machine.

  In addition, valve passage openings that communicate with the compression chamber communication passage that communicates with the compression chamber are provided on both side surfaces of the valve passage. During the operation of the compressor, the refrigerant is sucked from the suction pipe, the valve overcomes the spring force by the suction pressure and hits the valve stop surface, and the sucked refrigerant passes through the valve passage opening, passes through the compression chamber communication passage, and passes through the compression chamber. to go into. When the compressor is stopped, the refrigerant tends to flow backward from the compression chamber to the outside of the compressor through the compression chamber communication passage, the valve passage opening, and the valve passage due to the differential pressure between the discharge pressure and the suction pressure. However, since the refrigerant that has passed through the spring and is introduced into the back surface of the valve pushes the valve back to the end face of the suction pipe and seals it, the backflow of the refrigerant can be prevented (for example, see Patent Document 1).

JP 2007-239474 A

By the way, recently, there is a tendency to increase the upper limit capacity while maintaining the same size of the compressor, and the refrigerant flow rate is larger than the previous upper limit. As the refrigerant flow rate increases, the amount of refrigerant that flows backward immediately after the operation stops also increases. For this reason, when the amount of refrigerant flowing backward increases, the impact force or pressure applied to the spring increases, and there is a problem that the spring comes off from the valve passage and protrudes to the valve passage opening.
In order to solve this problem, in the compressor described in Patent Document 1, among the valve passage openings provided on both side surfaces of the valve passage, the valve passage opening on the side opposite to the compression chamber communication passage side is disposed in the compression chamber. A wall for preventing spring protrusion is formed at a position between the valve passage opening and the valve stop surface on the side surface of the valve passage on the side of the valve passage opening that is formed smaller than the valve passage opening on the communication passage side. It is supposed to be provided.

  However, the reverse flow of the refrigerant occurs not only when the operation is stopped but also during the reverse phase operation. The reverse phase operation occurs when the lead wire connection to the connection terminal with the electric motor driving the compressor, usually a glass-sealed terminal, which is abbreviated as a glass terminal, is mistaken. When such a reverse phase operation occurs, the compressor rotates reversely and the refrigerant forcibly flows backward, so that the spring protrudes. However, Patent Document 1 does not take any measures in particular during the reverse phase operation.

As described above, when the flow rate of the refrigerant flowing backward increases when the operation is stopped or in reverse phase operation, the spring breaks down due to the high-speed refrigerant hitting the spring while the valve is pushed back, and the spring end face is the valve passage opening. There is a problem that the spring protrudes from the valve passage opening in the worst case.
Furthermore, the spring protrudes into the valve passage opening and the opening / closing operation of the valve is hindered, or the reverse rotation noise is generated and the refrigeration oil is taken out of the machine, the bearing is insufficiently lubricated, and the bearing reliability is reduced. When the spring protrudes into the valve passage opening, the spring is caught in the compression chamber, causing a compressor lock.

  The present invention has been made in view of the above-described problems. By improving the valve structure described in Patent Document 1, the spring from the valve passage can be against reverse flow during reverse-phase operation of the compressor. The object is to obtain a compressor that does not protrude.

A compressor according to the present invention includes a compression mechanism that compresses a refrigerant introduced into a sealed container in a compression chamber, and an electric motor element that drives the compression mechanism, and is provided through the sealed container. A valve passage communicating with a suction pipe and a compression chamber communication passage communicating with the compression chamber is provided in the compression mechanism section;
A slidable valve in the valve passage, a spring for urging the valve against the valve seat surface of the suction pipe, and the spring is held when the refrigerant is sucked from the suction pipe. A valve stop surface for stopping the valve that is pressed against the spring force of the spring by suction pressure;
A first valve passage opening and a second valve passage opening communicating with the compression chamber communication passage are provided on both side surfaces of the valve passage;
A first valve passage opening on the compression chamber communication passage side is formed smaller than a second valve passage opening on the opposite side to the compression chamber communication passage, and on the side surface of the valve passage, the first valve passage opening and the A spring protrusion preventing wall is provided at a position between the valve stop surface and a valve passage upper communication passage that bypasses the valve passage communicates with the second valve passage opening and the first valve passage opening. It is provided.

  In the compressor of the present invention, a valve passage communicating with a suction pipe provided through the sealed container and a compression chamber communication path leading to a compression chamber for compressing the refrigerant introduced into the sealed container is used as the compression mechanism section. A first valve passage opening and a second valve passage opening communicating with the compression chamber communication passage are provided on both side surfaces of the valve passage, and the first valve passage opening on the compression chamber communication passage side is connected to the compression chamber communication passage. Is formed smaller than the second valve passage opening on the opposite side of the valve passage, and on the side surface of the valve passage, a spring protruding prevention wall is provided at a position between the first valve passage opening and the valve stop surface, and the valve passage is bypassed. Since the valve passage upper communication passage to be communicated is provided in communication with the second valve passage opening and the first valve passage opening, the amount of refrigerant flowing backward when the compressor is stopped increases or the refrigerant flows during reverse phase operation. Forcibly backflow or the spring tries to protrude from the valve passage It is possible to reliably prevented.

It is a longitudinal cross-sectional view of the scroll compressor in Embodiment 1 of this invention. (A) is an explanatory view showing the shape of the valve passage opening when stopped, (b) is an explanatory view showing the shape of the valve passage opening during operation, (c) (B) is explanatory drawing which looked at the side, (d) is AA sectional drawing of (c).

Embodiment 1 FIG.
With reference to FIG.1 and FIG.2, the scroll compressor in Embodiment 1 of this invention is demonstrated. In FIG. 1, 1 is a fixed scroll, and the outer peripheral part is fastened to the guide frame 15 by a bolt (not shown). A plate-like spiral tooth 1b is formed on one surface (lower side in FIG. 1) of the base plate portion 1a, and at the same time, two Oldham guide grooves 1c are formed on a substantially straight line. A claw 9b of the Oldham ring 9 is engaged with the Oldham guide groove 1c so as to be slidable back and forth.

  Further, as shown in FIG. 2, the fixed scroll 1 is provided with a compression chamber communication passage 1 k communicating with the compression chamber 1 d, and a suction pipe 10 a press-fitted through the compression chamber communication passage 1 k and the sealed container 10. A valve passage 1f that extends in the horizontal direction is provided in a direction perpendicular to the compression chamber communication passage 1k. A first valve passage opening 1j and a second valve passage opening 1m communicating with the compression chamber communication passage 1k are provided on both side surfaces of the valve passage 1f. The refrigerant flowing in through the suction pipe 10a flows through the first valve passage opening 1j on the compression chamber communication path 1k side to the compression chamber communication path 1k, and the second side on the opposite side of the compression chamber communication path 1k. The flow passes through the valve passage opening 1m, flows through the valve passage upper communication passage 1n bypassing the valve passage 1f, and flows into the compression chamber communication passage 1k. Further, the valve 17 is provided to slide inside the valve passage 1f.

Further, the valve 17 is biased by a spring 18 so as to be closed in the direction of the suction pipe 10a. The valve 17 stops at the end surface serving as a valve seat surface of the suction pipe 10a and is sealed to prevent the refrigerant from flowing backward. The side surface has a tapered shape so that the spring end surface portion 18a can easily fit in the valve stop surface 1g which is the terminal seat surface of the valve passage 1f.
Further, the valve stop surface 1g is provided with a high-pressure refrigerant introduction groove 1h which is a relief groove for guiding the refrigerant which has flowed back during operation stop or reverse phase operation to the rear end face of the valve 1f.

  Further, with respect to the first valve passage opening 1j and the second valve passage opening 1m provided on both side surfaces of the valve passage 1f, as shown in FIG. 2, the first valve passage opening on the compression chamber communication passage 1k side is provided. 1j is formed smaller than the second valve passage opening 1m opposite to the compression chamber communication passage 1k, and further, on the side surface of the valve passage 1f, the first valve passage opening 1j having a small opening and the spring end face portion 18a. A spring protruding prevention wall 11 is provided at a position between the valve stop surface 1g with which the valve contacts. The second valve passage opening 1m having a large opening opposite to the compression chamber communication passage 1k and the first valve passage opening 1j are formed by the valve passage upper communication passage 1n that bypasses the valve passage 1f as described above. Communicate.

Further, when the compressor is in operation, the terminal portion of the first valve passage opening 1j having a small opening on the compression chamber communication passage 1k side is located between the side surfaces of the valve 17 when the valve 17 is seated on the valve stop surface 1g. Is set.
Furthermore, the area of the two valve passage openings 1j and 1m provided on both side surfaces of the valve passage 1f is such that the refrigerant flows smoothly from the suction pipe 10a into the compression chamber communication passage 1k during operation. It is formed larger than the inner diameter area.

Reference numeral 2 denotes an orbiting scroll, and 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. The spiral tooth 1a and the plate-like spiral tooth 2b of the orbiting scroll 2 geometrically form a compression chamber 1d. 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 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 periphery of the base plate 2a of the orbiting scroll 2 in a substantially straight line. A claw 9a of the Oldham ring 9 is engaged with the groove 2e so as to be slidable back and forth. The base plate 2a is provided with an orbiting scroll extraction hole 2j that penetrates the compression chamber 1d and the thrust surface 2d, and has a structure for extracting refrigerant gas during compression 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 electric motor stator 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.

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 1e of the fixed scroll 1 by the notch 15c provided on the outer peripheral portion. A flow path for guiding the refrigerant gas to the discharge pipe 10b provided between the compression mechanism (1, 2, 3, 15) and the electric motor element (7, 8) is secured.
The notch 15c is provided at a position opposite to the discharge pipe 10b. The guide frame 15 has two cylindrical grooves 15a and 15b that engage 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 that store the sealing material. There are provided upper and lower sealing materials 16a and 16b, 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 16a and 16b communicates only with the communication passage 3s of the compliant frame 3. The refrigerant gas in the middle of compression supplied from the swing scroll extraction hole 2j is sealed.

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. Further, 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 below the main shaft portion 4c.
Further, 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. Between the sub-shaft portion 4d and the main shaft 4c, the motor rotor 8 is baked. It is fitted. An upper balancer 8a is fixed to the upper end surface of the motor rotor 8, and a lower balancer 8b is fixed to the lower end surface, and static balance and dynamic balance are achieved by a total of three balancers together with the spindle balancer 4e described above. ing.
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 in the oil sump 10g at the bottom of the sealed container 10 is sucked up. Further, a glass terminal 10 f is installed on the side surface of the sealed container 10, and a lead wire from the motor stator 7 is joined.

Next, the basic operation of the high pressure shell type frame compliant scroll compressor will be described.
During the operation of the compressor, as shown in FIG. 2 (b), the suction refrigerant is sucked from the suction pipe 10a, and the valve 17 overcomes the spring force by the suction pressure and is pushed down to the vicinity of the valve stop surface 1g, and the suction refrigerant is fixed. It enters the compression chamber 1d formed by the plate-like spiral teeth 1b of the scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2.
The orbiting scroll 2 driven by the electric motor stator 7 decreases the volume of the compression chamber 1d with an eccentric orbiting motion (this action is called a compression stroke).
Due to this compression stroke, the suction refrigerant becomes high pressure and is discharged into the sealed container 10 from the discharge port 1 e 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 through the communication passage 3s of the compliant frame 3 from the swing scroll extraction hole 2j of the swing scroll 2, and the frame space 15f Maintain an intermediate pressure atmosphere. The high-pressure discharge gas fills the sealed container 10 with a high-pressure atmosphere and is discharged from the discharge pipe 10b to the outside of the compressor.

The refrigerating machine oil 10e accumulated in the oil sump 10g at the bottom of the hermetic container 10 is guided to the swing bearing space 4b through the oil supply hole 4g penetrating the main shaft 4 in the axial direction due to the differential pressure.
The refrigerating machine oil 10e having an intermediate pressure due to the throttle action of the rocking bearing 2c fills the boss part space 2h surrounded by the rocking scroll 2 and the compliant frame 3, and connects the boss part space 2h and the low-pressure atmosphere space. It is led to a low pressure space via a pressure regulating valve (not shown) and sucked into the compression chamber 1d together with a low pressure refrigerant gas.
The refrigerating machine oil 10e is discharged into the sealed container 10 from the discharge port 1e together with the high-pressure refrigerant gas by the compression stroke.

  When the operation of the compressor is stopped, as shown in FIG. 2A, the first valve passage opening 1j on the compression chamber communication passage 1k side is smaller than the second valve passage opening 1m on the opposite side to the compression chamber communication passage 1k. The spring passage prevention wall 11 is provided at a position between the first valve passage opening 1j having a small opening and the valve stop surface 1g on the side surface of the valve passage 1f. A bypass valve passage upper communication passage 1n is provided to connect the second valve passage opening 1m and the first valve passage opening 1j. Therefore, the refrigerant having a high flow rate does not directly hit the spring 18 from the side opposite to the compression chamber communication path 1k side, and the refrigerant having a high flow rate is blocked by the spring protrusion prevention wall 11 from the compression chamber communication path 1k side. Since it does not directly hit the spring 18, as described above, the amount of refrigerant that flows backward when the compressor is stopped is large when the upper limit capacity is increased while the size of the compressor remains the same, and the refrigerant flow rate is larger than the previous upper limit. Or the compressor reversely rotates due to reverse phase operation caused by incorrect lead wire connection to the glass terminal 10f, and the refrigerant is forced to reversely flow. As a result of the contact, the spring 18 is violated, and the spring end surface portion 18a tries to protrude from the first valve passage opening 1j on the compression chamber communication passage 1k side, but the protrusion of the spring end surface portion 18a is for preventing the spring from protruding. Because it is blocked by 1l, so that the protrusion of the valve passage opening 1j of the spring end surface portion 18a is reliably prevented.

Accordingly, the valve 17 can move smoothly without delay in closing, the reverse sound due to the delay in closing the valve 17 can be prevented, and the refrigerating machine oil can be prevented from being taken out of the compressor. Can be prevented.
Further, in the compressor according to the present invention, since the spring protrusion preventing wall 11 is provided, the protrusion of the spring end face portion 18a is blocked by the spring protrusion preventing wall 11l, so that the valve passage opening of the spring end face portion 18a is prevented. Protrusion from the portion 1j is prevented, and the compressor lock due to spring engagement in the compression chamber 1d due to the protrusion of the spring 18 can be prevented.

  Further, when the compressor is in operation, the end portion of the first valve passage opening 1j on the compression chamber communication passage 1k side is set so as to be between the side surfaces of the valve 17 when the valve 17 is seated on the valve stop surface 1g. The second valve passage opening 1m opposite to the compression chamber communication passage 1k is communicated with the first valve passage opening 1j by the valve passage upper communication passage 1n that bypasses the valve passage 1f. Since the refrigerant having a high flow rate does not directly hit the spring 18 from the side opposite to the chamber communication path 1k side, the end of the first valve path opening 1j can be set up to the valve stop surface, and the two valve paths during operation can be set. The area of the openings 1j and 1m can be formed larger than the inner diameter area of the suction pipe 10a, and a compressor that can sufficiently secure the suction flow path area while preventing the spring end surface portion 18a from protruding is established.

  The compressor according to the first embodiment described above is a high-pressure shell type frame compliant scroll compressor, but may be provided with a valve mechanism on the suction side to prevent reverse rotation as in the first embodiment described above. For example, the same effect can be obtained with a scroll compressor, a rotary compressor, and other compressors.

  DESCRIPTION OF SYMBOLS 1 Fixed scroll, 1a Base plate part, 1b Plate-shaped spiral tooth, 1c Oldham guide groove, 1d Compression chamber, 1e Discharge port, 1f Valve passage, 1g Valve stop surface, 1h High-pressure refrigerant introduction groove, 1j First valve passage opening 1k compression chamber communication passage, 1l spring protrusion prevention wall, 1m second valve passage opening, 1n valve passage upper communication passage, 2 swing scroll, 2a base plate portion, 2b plate spiral tooth, 2c swing bearing, 2f Boss part, 2j Orbiting scroll extraction hole, 2k Thrust bearing side opening, 3 Compliant frame, 3a Thrust bearing, 3c Main bearing, 3d 3e Upper and lower cylindrical surface, 3h Sub main bearing, 3s Connecting passage, 4 Main shaft, 4b Oscillating bearing space, 4c main shaft, 4d secondary shaft, 4e main shaft balancer, 4f oil pipe, 4g oiling hole, 6 subframe, 6a secondary shaft 7 Motor stator, 8 Motor rotor, 8b Lower balancer, 9 Oldham ring, 9a 9b Oldham ring claw, 10 Sealed container, 10a Suction pipe, 10b Discharge pipe, 10e Refrigerating machine oil, 10f Glass terminal, 10g Oil sump, 15 guide frame, 15a 15b cylindrical surface, 15c notch, 15f frame space, 16a 16b upper and lower sealing materials, 17 valve, 18 spring, 18a spring end surface.

Claims (3)

A compression mechanism that compresses the refrigerant introduced into the sealed container in a compression chamber, and an electric motor element that drives the compression mechanism, and communicates with a suction pipe provided through the sealed container and the compression chamber. A valve passage communicating with the compression chamber communication passage is provided in the compression mechanism section;
A slidable valve in the valve passage, a spring for urging the valve against the valve seat surface of the suction pipe, and the spring is held when the refrigerant is sucked from the suction pipe. A valve stop surface for stopping the valve that is pressed against the spring force of the spring by suction pressure;
A first valve passage opening and a second valve passage opening communicating with the compression chamber communication passage are provided on both side surfaces of the valve passage;
A first valve passage opening on the compression chamber communication passage side is formed smaller than a second valve passage opening on the opposite side, and the side surface of the valve passage is between the first valve passage opening and the valve stop surface. And a valve passage upper communication passage that bypasses the valve passage is provided in communication with the second valve passage opening and the first valve passage opening. Compressor.   2. The compressor according to claim 1, wherein when the compressor is operated, a terminal portion of the first valve passage opening is set to be between the side surfaces of the valve when the valve is seated on the valve stop surface. Compressor.   3. The compressor according to claim 1, wherein an area of two valve passage openings provided on both side surfaces of the valve passage is larger than an inner diameter area of the suction pipe.

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