JP4081732B2 - Vane type compressor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a vane type compressor, and more particularly to a vane type compressor that can prevent the generation of noise due to so-called liquid compression (oil compression) at the time of startup.
[0002]
[Prior art]
Some conventional vane compressors are equipped with a pressure control valve that allows the refrigerant gas in the discharge chamber to escape to the suction chamber when the operation of the compressor is stopped (equal pressure between the discharge chamber and the suction chamber). (Kaihei 7-189971).
[0003]
The pressure control valve is provided in the middle of the gas passage that connects the discharge chamber and the suction chamber. The pressure control valve includes a ball-shaped valve body and a compression spring that pushes the valve body in the valve closing direction.
[0004]
During operation of the compressor, the valve body is in close contact with the valve seat, and the gas passage is blocked. That is, the refrigerant gas in the discharge chamber does not escape to the suction chamber through the gas passage.
[0005]
On the other hand, when the compressor stops and the pressure in the discharge chamber decreases, the valve body is separated from the valve seat, and the refrigerant gas in the discharge chamber escapes to the suction chamber through the gas passage.
[0006]
As a result, the force for pumping the lubricating oil (pressure in the discharge chamber) decreases, so that the amount of lubricating oil that enters the inner part of the vane groove is suppressed, and noise due to liquid compression at the time of restart is reduced.
[0007]
[Problems to be solved by the invention]
However, if the spring force of the compression spring is large, the pressure control valve is difficult to close, and the discharge performance at the time of start-up is reduced. Conversely, if the spring force of the compression spring is small, the pressure control valve is difficult to open at the time of stop, Liquid compression cannot be avoided reliably.
[0008]
As described above, in the conventional vane type compressor, it is difficult to reliably avoid the liquid compression without deteriorating the discharge performance at the start-up.
[0009]
The present invention has been made in view of such circumstances, and an object thereof is to provide a vane compressor that can reliably avoid liquid compression without deteriorating discharge performance at the time of startup.
[0010]
[Means for Solving the Problems]
In order to solve the above-described problem, a vane type compressor according to a first aspect of the present invention includes a rotor rotatably accommodated in a cam ring, a plurality of vane grooves provided on an outer peripheral surface of the rotor, and the vane grooves. Between the vane accommodated in a slidable manner, a first side member fixed to one of the cam rings, a second side member fixed to the other of the cam rings, and the vanes that follow each other in the rotational direction of the rotor A compression chamber formed in the pressure chamber, a high-pressure chamber in which the refrigerant gas discharged from the compression chamber is accommodated, and a lubricating oil that supplies lubricating oil to the interior of the vane groove using the pressure of the high-pressure chamber In the vane type compressor, comprising: a supply mechanism; and a valve accommodating chamber that communicates with the high pressure chamber and accommodates a discharge valve that opens and closes according to the pressure of the compression chamber. With a predetermined cross-sectional area Characterized in that it comprises a.
[0011]
When the operation of the compressor is stopped, the lubricating oil tries to enter the inner part of the vane groove in the process of balancing the pressure inside the compressor, but the passage having a predetermined cross-sectional area that connects the valve storage chamber and the compression chamber The pressure in the vane groove and the pressure in the low pressure chamber rises rapidly by allowing the refrigerant gas in the discharge chamber to escape to the compression chamber, and the pressure inside the compressor quickly balances. The amount of lubricating oil that enters is suppressed. As a result, it is possible to reduce noise due to liquid compression when the operation of the compressor is restarted next time.
[0012]
A vane type compressor according to a second aspect of the present invention is the vane type compressor according to the first aspect of the present invention, wherein the passage is a groove formed in one end face of the cam ring.
[0013]
As described above, since the passage is constituted by the groove formed on the one end surface of the cam ring, the processing of the passage is easy.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings.
[0015]
1 is a longitudinal sectional view of a vane compressor according to an embodiment of the present invention, FIG. 2 is a view taken along the line II-II in FIG. 1, and FIG. 3 is a view showing a front side end face of the cam ring. Is a sectional view taken along line IV-IV in FIG. 3, and FIG. 5 is a perspective view of the cam ring.
[0016]
The vane compressor includes a cam ring 1, a front side member (first side member) 25 fixed to one of the cam rings 1, a rear side member (second side member) 20 fixed to the other of the cam ring 1, A rotor 2 accommodated rotatably in the cam ring 1 and a drive shaft 7 of the rotor 2 are provided. The drive shaft 7 is rotatably supported by bearings 8 and 9.
[0017]
The front side member 25 includes a front side block 3 fixed to the front side end surface 1c of the cam ring 1 and a front head 5 fixed to the front side end surface of the cam ring 1 in a state of surrounding the front side block 3. ing.
[0018]
The front head 5 is provided with a refrigerant gas outlet (not shown). The refrigerant gas in the discharge chamber (high pressure chamber) 10 is sent to the condenser side (not shown) through this discharge port. The discharge chamber 10 is formed by the inner wall surface of the front head 5, the front side end surface of the front side block 3, and the front side end surface 1 c of the cam ring 1. High-pressure refrigerant gas discharged from a compression chamber 12a described later flows into the discharge chamber 10, and lubricating oil separated from the refrigerant gas accumulates at the bottom of the discharge chamber 10.
[0019]
The front side block 3 is provided with a discharge passage 3a that allows the discharge chamber 10 and a valve storage chamber 1a described later to communicate with each other.
[0020]
The rear side member 20 is composed only of the rear head 6 fixed to the rear side end surface of the cam ring 1 via an O-ring 22. The rear head 6 is formed with a refrigerant gas suction port 6 a, and the suction port 6 a communicates with the suction chamber 11.
[0021]
As shown in FIG. 2, two upper and lower compression spaces 12 are formed between the inner peripheral surface of the cam ring 1 and the outer peripheral surface of the rotor 2. A plurality of vane grooves 13 are provided in a substantially radial direction on the outer peripheral surface of the rotor 2, and vanes 14 are slidably inserted into the vane grooves 13. The compression space 12 is partitioned by the vanes 14 to form a plurality of compression chambers 12 a, and the volume of each compression chamber 12 a is changed by the rotation of the rotor 2.
[0022]
A valve accommodation chamber 1a for accommodating a discharge valve 19 described later is provided on the front side end face 1c of the cam ring 1 (only one valve accommodation chamber 1a is visible in FIG. 1). The valve storage chamber 1a and the compression space 12 communicate with each other via a discharge port 16 (only one discharge port 16 is visible in FIG. 1).
[0023]
As shown in FIG. 5, the valve accommodating chamber 1a accommodates a discharge valve 19 having a substantially cylindrical shape (C-shaped section) and a valve presser 32 having a substantially cylindrical shape (C-shaped section). The valve presser 32 is accommodated so as to be surrounded by the discharge valve 19 (see FIG. 2). One end portion (one end portion in the circumferential direction) of the valve presser 32 and the valve holder 31 is fixed by a bolt 33. The bolt 33 is screwed into the screw hole 1 b of the cam ring 1 through the O-ring 31. Before the bolt 33 is screwed, if the through hole 32a, 19a of the valve presser 32 and the discharge valve 19 and the screw hole 1b are opposed to each other, the tip of the bolt 33 when the bolt 33 is screwed into the screw hole 1b. The portion passes through the valve presser 32 and the through holes 32a and 19a of the discharge valve 19, and protrudes into the valve housing chamber 1a (see FIGS. 1 and 2). The discharge valve 19 opens and closes according to the pressure in the compression chamber 12a to open and close the discharge port 16. The valve presser 32 regulates the valve opening amount of the discharge valve 19.
[0024]
Further, a groove (passage) 40 is provided on the front end face 1c of the cam ring 1 to allow the valve housing chamber 1a and the compression chamber 12 to communicate with each other. The cross-sectional area (predetermined cross-sectional area) of the groove 40 is, for example, 0,05 to 0,5 mm ² . The groove 40 and the discharge port 16 are substantially aligned along the center axis of the rotor. Strictly speaking, the groove 40 and the counter bore 50 of the discharge port 16 (the counterbore hole around the opening edge of the discharge port 16) are located behind the starting end portion 50a in the rotor rotation direction (see FIG. 5). ).
[0025]
A suction port (not shown) through which low-pressure refrigerant gas is fed from the suction chamber 11 to the compression chamber 12a is provided on the rear side end face of the cam ring 1.
[0026]
Back pressure grooves 35, 36 communicating with the back part (back pressure chamber) 13 a of the vane groove 13 from the start of suction to the end of compression on the rear side end face of the front side block 3 and the front side end face of the rear head 3. Are provided respectively. The back pressure grooves 35 and 36 are two arc-shaped grooves provided along the circumferential direction. Lubricating oil at the bottom of the discharge chamber 10 is supplied to the back pressure grooves 35 and 36 using the pressure of the discharge chamber 10, and the back pressure chamber 13 a communicates with the back pressure grooves 35 and 36 by the rotation of the rotor 2. Sometimes the lubricating oil is supplied from the back pressure grooves 35 and 36 to the back pressure chamber 13a.
[0027]
FIG. 6 is an enlarged cross-sectional view showing the start valve.
[0028]
The front side block 3 is provided with a communication passage 41 that allows the discharge chamber 10 and the back pressure groove 35 on the front side to communicate with each other. The communication passage 41 is provided with an activation on-off valve 42 that opens when the pressure in the discharge chamber 10 does not reach a predetermined value and closes when the pressure reaches the predetermined value. The activation opening / closing valve 42 urges the ball valve body 42a and the ball valve body 42a moving between the valve opening position away from the valve seat 41a and the valve closing position seated on the valve seat 41a to the open position side. A winding spring 42b and a pin 42c for holding the ball valve body 42a in the valve open position are provided.
[0029]
Next, the operation of this vane type compressor will be described.
[0030]
When the rotational power of an engine (not shown) is transmitted to the drive shaft 7, the rotor 2 rotates. Refrigerant gas flowing out from the outlet of an evaporator (not shown) enters the suction chamber 11 through the suction port 6a, and is sucked into the compression space 12 from the suction chamber 11 through the suction port.
[0031]
The compression space 12a is partitioned by vanes 14 that follow each other in the rotor rotation direction to form five compression chambers 12a. However, the volume of each compression chamber 12a changes as the rotor 2 rotates. The refrigerant gas confined between the vanes 14 is compressed, and the compressed refrigerant gas flows to the valve accommodating chamber 1a through the discharge port 16. The refrigerant gas in the valve storage chamber 1a flows to the discharge chamber 10 through the discharge passage 3a and is discharged from the discharge port to the condenser side. In addition, the refrigerant gas that has flowed into the discharge chamber 10 is oil-separated, and lubricating oil accumulates at the bottom of the discharge chamber 10.
[0032]
When the compressor is activated, the ball valve element 42a of the activation opening / closing valve 42 is opened by the urging force of the winding spring 42b until the rotor 2 starts rotating and the pressure in the discharge chamber 10 reaches a predetermined value. The communication path 41 is opened. Therefore, the refrigerant gas in the discharge chamber 10 is fed into the back pressure chamber 13a in the region from the vicinity of the suction start position to the compression end position through the communication passage 41 and the back pressure groove 35, and the vane 14 is discharged from the vane groove 13. It becomes easy to jump out.
[0033]
When the pressure in the discharge chamber 10 reaches a predetermined value after starting the compressor and enters a steady operation state, the ball valve element 42a moves in the valve closing direction against the urging force of the winding spring 42b and is seated on the valve seat 41a. Then, the communication path 41 is blocked.
[0034]
Further, when the operation of the compressor is stopped, the lubricating oil enters the back pressure chamber 13a in the process of balancing the pressure inside the compressor. However, since the groove 40 is provided in the front side end face 1c of the cam ring 1 as described above, the refrigerant gas in the discharge chamber 10 escapes to the compression chamber 12a through the groove 40, so that the front side block 3 and the rotor 2 The refrigerant gas flows into the back pressure chamber 13a from the gap between the pressure and the pressure in the back pressure chamber 13a quickly increases. As a result, the start opening / closing valve 42 opens in a short time, and the pressures in the chambers 10, 11, 13a are quickly balanced. Thus, since the time from when the operation is stopped to when the start opening / closing valve 42 is opened is short and the amount of lubricating oil entering the back pressure chamber 13a is small in the process of pressure balance, the liquid when the compressor operation is resumed is reduced. Noise due to compression can be reduced.
[0035]
During the operation of the compressor, the high-pressure refrigerant gas in the valve housing chamber 1a escapes to the compression chamber 12a through the groove 40. However, as described above, the passage cross-sectional area of the groove 40 is small and the gas in the compression chamber 12a is in operation. Is in the compression process, the average pressure difference with the valve accommodating chamber 1a is small, the amount of refrigerant gas escaping through the groove 40 is small, and does not greatly affect the discharge performance.
[0036]
According to this embodiment, when the operation of the compressor is stopped as described above, the refrigerant gas in the discharge chamber 10 is released to the compression chamber 12a through the groove 40 having a predetermined passage cross-sectional area formed in the front side end surface 1c of the cam ring 1. The pressure in the back pressure chamber 13a is quickly increased, the time until the start valve 42 is opened is shortened, and the amount of lubricating oil entering the back pressure chamber 13a in the process of balancing the pressure inside the compressor is reduced. Therefore, it is possible to reliably avoid liquid compression during restart without deteriorating the discharge performance.
[0037]
Further, since the groove 40 is provided as a passage for communicating the valve storage chamber 1a and the compression chamber 12a, the processing of the passage is easy, and the manufacturing cost can be reduced.
[0038]
As a method for leaking refrigerant gas from the valve accommodating chamber 1a to the compression chamber 12a, a method for adjusting the sheet property of the discharge valve 19 with respect to the seat surface without adjusting the passage (for example, adjusting the roughness of the seat surface). However, this embodiment in which the groove 40 is provided as a passage for communicating the valve accommodating chamber 1a and the compression chamber 12a is superior in terms of controlling the amount of leakage.
[0039]
Although the vane type compressor of this embodiment is provided with the starting on-off valve 42, the present invention is also applicable to a vane type compressor not provided with the starting on-off valve 42.
[0040]
【The invention's effect】
As described above, according to the vane type compressor of the first aspect of the present invention, it is possible to reliably avoid the liquid compression without deteriorating the discharge performance at the start-up.
[0041]
According to the vane type compressor of the invention of claim 2, the processing of the passage is easy, and the manufacturing cost can be reduced.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a vane compressor according to an embodiment of the present invention.
FIG. 2 is a view taken along the line II-II in FIG.
FIG. 3 is a view showing a front side end face of the cam ring.
4 is a cross-sectional view taken along the line IV-IV in FIG. 3;
FIG. 5 is a perspective view of a cam ring.
FIG. 6 is an enlarged cross-sectional view showing an activation on-off valve.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Cam ring 1a Valve accommodation chamber 1c Front side end surface 2 of a cam ring Rotor 3 Front side block 5 Front head 6 Rear head 10 Discharge chamber 12a Compression chamber 13 Vane groove 13a Back pressure chamber 14 Vane 19 Discharge valve 20 Rear side member 25 Front Side member 40 groove

Claims (2)

A rotor rotatably accommodated in the cam ring, a plurality of vane grooves provided on the outer peripheral surface of the rotor, a vane slidably accommodated in the vane groove, and a first fixed to one of the cam rings 1 side member, 2nd side member fixed to the other of the said cam ring, the compression chamber formed between the said vanes mutually followed in the rotation direction of the said rotor, and the refrigerant gas discharged from the said compression chamber accommodates A high-pressure chamber, a lubricating oil supply mechanism that supplies lubricating oil to the interior of the vane groove using the pressure of the high-pressure chamber, and communicates with the high-pressure chamber, depending on the pressure of the compression chamber In a vane type compressor having a valve storage chamber in which a discharge valve that opens and closes is stored,
A vane-type compressor comprising a passage having a predetermined cross-sectional area that allows the valve storage chamber and the compression chamber to communicate with each other. 2. The vane type compressor according to claim 1, wherein the passage is a groove formed on one end face of the cam ring.

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