JP2007332931A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor capable of suppressing errors due to vibration and heat, and accurately detecting flow rate of a compressor. <P>SOLUTION: A flange member to be joined to a housing 11 is provided, and the flange member forms a flange passage between external refrigerant circuit 36 and a refrigerant passage within the housing 11. A variable displacement compressor has a movable element 53 that is movable in response to flow rate of a refrigerant gas in the flange passage, and has a magnet 57, and a detection sensor 60 for detecting a flux density of the magnet 57. The flange member has a movable element housing portion for housing the movable element 53, and the movable element 53 has a slide contact member for slidingly contacting with an inner wall surface of the movable element housing portion. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a variable capacity compressor, and in particular, includes a movable body that moves in response to a change in the flow rate of the refrigerant gas, detects the magnetic flux density of a magnet that the movable body has, and based on the detected magnetic flux density, The present invention relates to a variable displacement compressor that detects a gas flow rate.

  In general, conventionally known variable capacity compressors (hereinafter simply referred to as “compressors”) change the inclination angle of the swash plate by adjusting the opening of the capacity control valve, thereby reducing the discharge capacity. Is configured to change.

However, in the discharge capacity change control, there is a problem that the actual flow rate of the refrigerant gas cannot be known only by issuing a flow rate change command to the capacity control valve.
Further, when the discharge capacity is changed, the power of the compressor also changes, but the power of the compressor is currently estimated by a calculated value based on the flow rate command value.

Therefore, until the discharge capacity after the flow rate change command reaches the command value, the actual power of the compressor is different from the calculated value based on the flow rate command value, and an error occurs.
In particular, when the vehicle engine is compressed at the start of operation, the error becomes large.
For this reason, there is a state in which it is difficult to perform appropriate control, for example, it takes a long time to reach the required passenger compartment temperature or the burden on the engine on the vehicle side increases (see, for example, Patent Document 1).

If the flow rate of the refrigerant gas can be accurately detected in the compressor, the actual discharge capacity and power can be known by calculation, which is extremely useful.
Thus, for example, a method of detecting the flow rate of the compressor using an electronic flow meter as disclosed in Patent Document 2 is conceivable.

The electronic flow meter disclosed in FIG. 1 of Patent Document 2 is provided with a sliding guide above the movable part of the float (corresponding to a movable body) of the main body of the area flow meter, and provided on the upper surface of the float. A magnet is fixed through a rod.
Then, as the float moves up and down, the magnet is displaced up and down in the sliding guide.
A magnetic field of the magnet is formed on the outer wall of the sliding guide at a right angle to the thin film of the Hall element (corresponding to the detection sensor), and the magnet is disposed so as to be displaced in parallel with the thin film of the Hall element. The hall element is connected to the control means.

In addition, the electronic flow meter disclosed in FIG. 2 of Patent Document 2 is provided with a differential pressure detection unit connected to the high and low pressure guiding paths fixed before and after the orifice of the flow path. The portion is hermetically divided into two by a bellophram (corresponding to a movable body), and the pressure of the flow path in the orifice is transmitted to both sides of the bellophram, and the magnet extending to the bellophram is displaced by the differential pressure.
In addition, a hall element (corresponding to a detection sensor) is provided at right angles to the displacement direction of the magnet, and the magnet is configured to oppose the magnetic pole to the hall element. The hall element and the control means are connected.
Japanese Patent Laid-Open No. 2002-332962 Japanese Utility Model Publication No. 63-177715

However, when the flow meter disclosed in Patent Document 2 is simply applied to a compressor, the following problems are expected.
The magnet which is a movable body is in a state of being accommodated in the housing, but the movable body is easy to move in the reciprocating direction, that is, in a state where the movable body moves sensitively to the fluctuation of the differential pressure, The movable body is likely to move relatively easily only by receiving the vibration of the compressor.
In particular, in a configuration in which the movable body is pressed in one direction by an elastic means such as a spring, when the vibration that causes the movable body to resonate is received from the compressor, the resonating movable body greatly reciprocates via the elastic means.
Movement of the movable body due to vibration prevents accurate flow rate detection of the compressor.

Further, in order to accurately detect the flow rate of the compressor separately from the vibration of the compressor, for example, the clearance between the movable body and the movable body accommodating portion is set strictly, and the high pressure side in the movable body accommodating portion is changed to the low pressure side. It is necessary to prevent leakage of refrigerant gas.
However, when the materials forming the movable body and the movable body accommodating portion are different, the clearance varies due to the difference in thermal expansion between the two.
The fluctuation of the clearance may cause a phenomenon that the position of the movable body is not determined according to the clearance, and may cause an inaccurate flow rate detection of the compressor.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a variable capacity compressor capable of accurately detecting the flow rate of a compressor while suppressing errors due to the effects of vibration and heat. On offer.

  In order to achieve the above object, according to the present invention, a refrigerant passage including a suction pressure region and a discharge pressure region is formed in a housing having a cylinder bore and a crank chamber, a piston is accommodated in the cylinder bore, and a slant is formed in the crank chamber. A flange member is provided that is accommodated in the housing and is joined to the housing. The flange member forms a flange passage between the external refrigerant circuit and the refrigerant passage in the housing, and the flow rate of the refrigerant gas in the flange passage is increased. And a variable capacity compressor having a movable body that has a magnet and a detection sensor that detects a magnetic flux density of the magnet, and the flange member has a movable body housing portion that houses the movable body, The movable body includes a sliding contact member that is in sliding contact with an inner wall surface of the movable body housing portion.

According to the present invention, the sliding contact member provided on the movable body is positioned in the clearance between the movable body, which is an element related to flow rate detection, and the movable body housing portion.
The frictional force generated between the sliding contact member and the movable body housing portion prevents the movable body from moving due to vibration.
The movement of the movable body caused by vibration is suppressed by the frictional force between the sliding contact member and the movable body accommodating portion, and the movable body moves in the movable body accommodating portion based on the flow rate differential pressure. Yes.

In the above variable displacement compressor, the movable body has an outer peripheral surface having a circular cross section, the movable body housing portion has an inner wall surface having a circular cross section corresponding to the outer peripheral surface, and the outer peripheral surface includes A mounting groove for mounting the sliding member may be formed.
In this case, the sliding member is held with respect to the movable body via the mounting groove.

In the above variable displacement compressor, the mounting groove is an annular groove, the sliding member is a C-ring formed of an elastic material, and the sliding member is movable from the annular groove. You may have the urging | biasing force which urges | biases the said sliding contact member to the inner wall face of a body accommodating part.
In this case, since the sliding contact member is a C-ring, even if the flange member and the movable body forming the movable body housing portion are made of different materials, the sliding contact member absorbs the variation in clearance due to thermal expansion. be able to.
The influence on the flow rate differential pressure due to the variation in the clearance can be suppressed, and accurate flow rate detection can be performed.
Since the sliding contact member is a C-ring, it performs a sealing function that partitions the high-pressure side and the low-pressure side of the movable body housing portion in which the movable body is housed, and suppresses leakage of refrigerant gas from the high pressure side to the low pressure side.

In the variable displacement compressor described above, the movable body may be pressed in one direction by a resilient means.
In this case, even if vibration that causes resonance of the movable body via the elastic means occurs in the compressor, the frictional force between the sliding contact member and the inner wall surface of the movable body accommodating portion causes resonance of the movable body via the elastic means. To prevent.

  ADVANTAGE OF THE INVENTION According to this invention, the error by the influence of a vibration and a heat | fever can be suppressed, and the variable capacity type compressor which performs the flow volume detection of a compressor correctly can be provided.

(First embodiment)
The variable capacity compressor (hereinafter simply referred to as “compressor”) according to the first embodiment of the present invention will be described below.
FIG. 1 shows an outline of a compressor embodying the present invention.
The compressor housing 11 includes a cylinder block 12, a front housing 13 joined to the front end of the cylinder block 12, and a rear housing 14 joined to the rear end of the cylinder block 12.
For convenience of explanation, the left side in FIG. 1 is the front side, and the right side is the rear side.

The cylinder block 12 and the front housing 13 define a crank chamber 15 as a control chamber in the housing 11.
A drive shaft 16 is rotatably disposed in the crank chamber 15.
The drive shaft 16 is operatively connected to an engine 17 mounted on the vehicle, and is rotationally driven by power supply from the engine 17.
In this embodiment, a configuration in which the power of the engine 17 is always transmitted to the drive shaft 16 is adopted, and the compressor is a clutchless variable displacement compressor.

In the crank chamber 15, a lug plate 18 is fixed on the drive shaft 16 so as to be integrally rotatable.
A swash plate 19 is accommodated in the crank chamber 15.
The swash plate 19 is fitted to the drive shaft 16 at a set inclination angle, is supported to be tiltable in the axial direction of the drive shaft 16 and is slidable on the drive shaft 16.
The hinge mechanism 20 is interposed between the lug plate 18 and the swash plate 19.
Accordingly, the swash plate 19 rotates synchronously with the lug plate 18 and the drive shaft 16 via the hinge mechanism 20 and tilts with respect to the axial direction of the drive shaft 16.
The inclination angle of the swash plate 19 is controlled by a capacity control valve 34 described later.

A plurality (only one is shown in FIG. 1) of cylinder bores 21 is formed in the cylinder block 12, and a single-headed piston 22 is accommodated in each cylinder bore 21 so as to be able to reciprocate.
Each piston 22 is anchored to the outer periphery of the swash plate 19 via a shoe 23.
Accordingly, the rotational motion of the swash plate 19 accompanying the rotation of the drive shaft 16 is converted into the reciprocating motion of the piston 22 via the shoe 23.

A valve / port forming body 24 is interposed between the cylinder block 12 and the rear housing 14, and is surrounded by the piston 22 and the valve / port forming body 24 on the back side (right side in FIG. 1) of the cylinder bore 21. The compressed chamber 25 is partitioned.
Inside the rear housing 14, a suction chamber 26 as a suction pressure region and a discharge chamber 27 as a discharge pressure region are defined.
The suction chamber 26 and the discharge chamber 27 are refrigerant passages in the compressor.

The refrigerant gas in the suction chamber 26 is compressed through the suction port 28 and the suction valve 29 formed in the valve / port formation body 24 as each piston 22 moves from the top dead center position to the bottom dead center position. Inhaled into chamber 25.
The refrigerant gas sucked into the compression chamber 25 is compressed to a predetermined pressure as the piston 22 moves from the bottom dead center position to the top dead center position, and the discharge port 30 formed in the valve / port forming body 24 and It is discharged into the discharge chamber 27 through the discharge valve 31.

By the way, a bleed passage 32 that connects the crank chamber 15 and the suction chamber 26 is formed in the cylinder block 12.
The extraction passage 32 is a passage for releasing the pressure of the crank chamber 15 to the suction chamber 26.
An air supply passage 33 that communicates between the discharge chamber 27 and the crank chamber 15 is formed across the cylinder block 12 and the rear housing 14.
The air supply passage 33 is a passage for supplying the pressure of the discharge chamber 27 to the crank chamber 15.
In the rear housing 14, a capacity control valve 34 is disposed in the supply passage 33.

The capacity control valve 34 communicates with the suction chamber 26 via the first pressure detection passage 35, and the opening degree of the capacity control valve 34 is adjusted according to the pressure in the suction chamber 26.
Then, by adjusting the opening of the capacity control valve 34, the amount of high-pressure refrigerant gas introduced into the crank chamber 15 through the air supply passage 33 and the refrigerant derived from the crank chamber 15 through the extraction passage 32. The balance with the gas lead-out amount is controlled, and the internal pressure of the crank chamber 15 is determined.
In accordance with the internal pressure in the crank chamber 15, the difference from the internal pressure in the cylinder bore 21 via the piston 22 is changed, and the inclination angle of the swash plate 19 with respect to the drive shaft 16 is changed.
As a result, the compressor can change the stroke of the piston 22, that is, the discharge capacity of the refrigerant gas.

For example, when the internal pressure of the crank chamber 15 decreases, the inclination angle of the swash plate 19 increases and the discharge capacity of the compressor increases.
A swash plate 19 indicated by a two-dot chain line in FIG. 1 shows a state of the maximum inclination angle in contact with the lug plate 18.
On the contrary, when the internal pressure of the crank chamber 15 increases, the inclination angle of the swash plate 19 decreases and the discharge capacity of the compressor decreases.
A swash plate 19 shown by a solid line in FIG. 1 shows a state of a minimum inclination angle.

The refrigerant circuit (refrigeration cycle) of the vehicle air conditioner includes a compressor as a part of the refrigerant circuit, and an external refrigerant circuit 36 connected to the discharge chamber 27 and the suction chamber 26 of the compressor.
For example, carbon dioxide or chlorofluorocarbon is used as the refrigerant.
The external refrigerant circuit 36 includes a condenser 37, a receiver tank 38, an expansion valve 39, and an evaporator 40 in order from the discharge chamber 27 side.
Further, a pressure sensor 41 for detecting the pressure of the refrigerant is disposed in the refrigerant passage connecting the condenser 37 and the receiver tank 38.
The detection signal of the pressure sensor 41 is transmitted to the amplifier 45 via the electrical connection line 42, the data input means 43 and the connection line 44.
The amplifier 45 controls the capacity control valve 34, and a discharge capacity change command from the amplifier 45 is transmitted to the capacity control valve 34 via the connection line 61.
The amplifier 45 has data relating to the flow rate of refrigerant gas from a magnetic sensor 60 described later, vehicle compartment temperature information from the data input means 43, refrigerant gas pressure data from the compressor pressure sensor 41, and the like.
Further, the amplifier 45 is connected to engine control means (not shown).

By the way, on the upper surface of the cylinder block 12, a flow rate detecting device shown in detail in FIGS.
The flow rate detection device is provided in a discharge flange 46 as a flange member joined to the outside of the cylinder block 12, and serves as a movable body 53 accommodated in the discharge flange 46 and a resilient means for pressing the movable body 53 to one side. The coil spring 56 and a magnetic sensor 60 as a detection sensor fixed to the surface of the discharge flange 46 are mainly configured.

The discharge flange 46 is detachably joined to the cylinder block 12 by a joining bolt (not shown).
A gasket 47 as a heat insulating material is interposed between the discharge flange 46 and the cylinder block 12.
The gasket 47 is formed of a heat insulating material made of rubber or resin, and makes it difficult to transfer the heat on the housing 11 side to the discharge flange 46.

In a state where the discharge flange 46 is joined to the cylinder block 12, a flange passage is formed inside the discharge flange 46.
As shown in FIG. 2, the flange passage includes a high pressure space 48a and a low pressure space 48b communicated with each other via a restriction 52 provided in a partition wall 46a of the discharge flange, a flow passage 51 communicated with the low pressure space 48b, and a low pressure space. The movable body accommodating part 49 which communicates with 48b, and the communicating path 50 which connects the movable body accommodating part 49 and the high voltage | pressure space 48a are included.
Since the partition wall 46a in the discharge flange 46 forms the throttle 52 of the flange passage, it corresponds to the throttle part, the high pressure space 48a is upstream of the partition wall 46a as the throttle part, and the low pressure space 48b is downstream of the throttle part. is there.
In the discharge flange 46, a bottomed cylindrical movable body accommodating portion 49 communicating with the high-pressure space 48a is formed through the communication passage 50, and the movable body 53 made of a spool slides within a certain distance. Being housed so that you can.
For this reason, the movable body accommodating portion 49 has a high pressure side pressure sensing chamber 49a communicating with the high pressure space 48a via the communication path 50 and a low pressure side pressure sensing chamber 49b communicating with the low pressure space 48b by the accommodated movable body 53. It is divided into.

As shown in FIGS. 2 to 4, the movable body 53 has a cylindrical shape having an upper end small diameter portion 54 and a lower end large diameter portion 55.
The upper end small diameter portion 54 has a gap with the inner wall surface of the movable body accommodating portion 49, and a magnet 57 is embedded in the upper end small diameter portion 54.
A concave portion 55a is formed in the lower end large diameter portion 55, and a coil spring 56 is provided in the concave portion 55a as a resilient means for urging the movable body 53 upward (one direction).
A perforated locking member 58 is attached to the inner wall surface of the movable body accommodating portion 49 near the low pressure space 48 b, and the locking member 58 prevents the movable body 53 and the coil spring 56 from coming off.

The coil spring 56 is set to have a spring constant so that when a differential pressure described later is applied to the movable body 53, the coil spring 56 is balanced at a position corresponding to the applied differential pressure.
It should be noted that the outer diameter of the lower end large diameter portion 55 substantially corresponds to the inner diameter of the movable body accommodating portion 49, and the clearance C between them is the sliding of the movable body 53 in the movable body accommodating portion 49 as shown in FIG. It is a gap that allows movement.

As shown in FIGS. 3 and 4, an annular groove 66 having a U-shaped cross section is formed on the outer peripheral surface of the lower end large diameter portion 55.
The annular groove 66 corresponds to a mounting groove, and makes one round of the outer peripheral surface of the lower end large diameter portion 55. A seal member 68 as a sliding contact member shown in FIG.
Although the external appearance of the seal member 68 is substantially annular, it has a notch 68a and therefore has a substantially C-shaped form. The seal member 68 is formed of a rubber-based material that is an elastic material.
The cross-sectional shape of the seal member 68 is a substantially square shape that substantially corresponds to the annular groove 66, but the term “substantially corresponds” here refers to a shape that allows the seal member 68 to be easily mounted in the annular groove 66.
The notch 68a is intended to absorb the expansion and contraction by the seal member 68 even if the movable body 53 expands or contracts due to temperature and the clearance C from the inner wall surface of the movable body accommodating portion 49 varies.

In a state where the movable body 53 in which the seal member 68 is mounted in the annular groove 66 is accommodated in the movable body accommodation portion 49, the seal member 68 generates a biasing force that expands toward the inner wall surface of the movable body accommodation portion 49.
Therefore, as shown in FIG. 4, a gap d is formed between the bottom surface of the annular groove 66 and the inner diameter surface of the seal member 68 facing the bottom surface.
The gap d similarly absorbs fluctuations in the clearance C due to thermal expansion and contraction of the movable body 53, similarly to the notch 68 a of the seal member 68.
Since the sectional shape of the annular groove 66 and the seal member 68 is substantially square, the seal member 68 is in surface contact with the inner wall surface of the movable body accommodating portion 49, and one wall surface of the annular groove 66 (the lower side in FIG. 4). Surface contact with (horizontal plane).
The step surface that becomes the boundary between the upper end small diameter portion 54 and the lower end large diameter portion 55 is a pressure receiving surface that receives the pressure of the high pressure space 48a, and the lower surface of the lower end large diameter portion 55 is the pressure receiving surface that receives the pressure of the low pressure space 48b.

A magnetic sensor 60 facing the magnet 57 of the movable body 53 is fixed to the upper surface of the discharge flange 46 by an attachment member 59.
The magnetic sensor 60 is a detection sensor that detects the magnetic flux density of the magnet 57.
A predetermined gap is provided between the magnetic sensor 60 and the discharge flange 46 so that the magnetic sensor 60 does not directly receive heat transfer on the housing 11 side.
Further, the mounting member 59 as a heat insulating material for holding the magnetic sensor 60 is formed of a heat insulating material made of rubber or resin, and prevents heat conduction to the magnetic sensor 60 through the mounting member 59.

The magnetic sensor 60 is connected to the amplifier 45 via a connection line 65.
Based on the output from the magnetic sensor 60, the amplifier 45 recognizes that the differential pressure between the high pressure space 48a and the low pressure space 48b is small when the distance between the magnetic sensor 60 and the magnet 57 approaches, and the distance from the magnet 57 increases. Has a function of recognizing that the differential pressure between the two 48a and 48b is large.
The high-pressure space 48a formed in the discharge flange 46 communicates with the discharge chamber 27 via discharge passages 62, 63, and 64 formed in the rear housing 14, as shown in FIG.
Accordingly, the high-pressure space 48 a can be supplied with the high-pressure refrigerant gas discharged from the discharge chamber 27.
2 is formed with a bolt through hole 67 for a through bolt for joining the front housing 13 and the rear housing 14. In the cylinder block 12 shown in FIG.

According to the above configuration, the supply of the high-pressure refrigerant gas causes the refrigerant gas to be introduced from the high-pressure space 48a to the low-pressure space 48b through the restriction 52, and the pressure of the refrigerant gas in the low-pressure space 48b is compared with that of the high-pressure space 48a. And is in a lowered state.
On the other hand, part of the high-pressure refrigerant gas in the high-pressure space 48 a is introduced into the high-pressure side pressure sensing chamber 49 a through the communication path 50.
On the other hand, a part of the low pressure gas in the low pressure space 48b is introduced into the low pressure side pressure sensing chamber 49b.
For this reason, the movable body 53 is moved into the movable body accommodating portion 49 by the flow rate differential pressure between the high pressure refrigerant gas received by the end surface of the upper end small diameter portion 54 and the low pressure refrigerant gas acting on the lower end large diameter portion 55. Slides up and down.
When the discharge capacity is changed by the control of the capacity control valve 34, the discharge capacity of the discharge chamber 27 changes, so that the flow rate differential pressure acting on the movable body 53 changes, and the movable body 53 changes according to the flow rate differential pressure. 3 move up or down.
For example, when the discharge capacity increases, the flow rate differential pressure increases, so that the movable body 53 moves downward in the case of FIG.

When the movable body 53 moves through the movable body housing portion 49, the seal member 68 mounted in the annular groove 66 is in sliding contact with the inner wall surface of the movable body housing portion 49.
The frictional force between the seal member 68 and the inner wall surface of the movable body accommodating portion 49 prevents excessive movement of the movable body 53 due to vibration or the like, and suppresses resonance of the movable body 53.
Further, the seal member 68 is in sliding contact with the inner wall surface of the movable body accommodating portion 49, and the seal member 68 receives a high pressure from the same high pressure region as the high pressure space 48a, so that the low pressure space 48b in the annular groove 66 is on the same low pressure region side. Since it is in contact with the surface, the high pressure region and the low pressure region in the movable body accommodating portion 49 are surely partitioned, and leakage of the refrigerant gas in the movable body accommodating portion 49 is prevented.
Then, due to the influence of temperature, for example, the discharge flange 46 forming the movable body accommodating portion 49 and the material of the movable body 53 are different, the clearance C between the both 46 and 53 varies, but the seal member 68 reduces the clearance C. Since it is always filled, it is easy to eliminate the effect of fluctuations in the flow differential pressure due to temperature.
Since the seal member 68 has the notch 68 a, the seal member 68 that tries to expand toward the inner wall surface of the movable body accommodating portion 49 even if the movable body 53 is thermally expanded or contracted is separated from the inner wall surface of the movable body accommodating portion 49. The sliding contact state can be maintained.
Furthermore, since the annular groove 66 has a sufficiently deep radial depth as compared with the radial thickness of the seal member 68, the influence of the expansion / contraction of the movable body 53 due to the temperature together with the notch 68 a of the seal member 68. The seal member 68 hardly receives.

If the movable body 53 moves according to the flow rate differential pressure, the magnetic flux density of the magnet 57 with respect to the magnetic sensor 60 changes.
Based on the magnetic flux density detected by the magnetic sensor 60, the flow rate of the refrigerant gas can be known.
The amplifier 45 calculates the discharge capacity in real time based on the flow rate data of the refrigerant gas obtained by the magnetic sensor 60, performs feedback control to the capacity control valve 34, and performs optimal discharge capacity control.
Further, since the flow rate of the refrigerant gas can be obtained, the torque of the compressor can be calculated, and the amplifier 45 performs feedback control according to the flow rate to the engine control means, and optimal engine speed control is performed. The

The compressor according to this embodiment has the following effects.
(1) Since the seal member 68 provided on the movable body 53 is located in the clearance C between the movable body 53 and the movable body accommodating portion 49, which is an element relating to flow rate detection, the seal member 68 and the movable body accommodating portion 49 Movement of the movable body 53 due to vibration can be prevented by the frictional force with the inner wall surface.
By suppressing or preventing the movement of the movable body 53 due to external vibration, the movable body 53 can move accurately based on the flow rate differential pressure, and the compressor can accurately detect the flow rate.
(2) The seal member 68 performs a sealing function to partition the high pressure side pressure sensitive chamber 49a and the low pressure side pressure sensitive chamber 49b of the movable body accommodating portion 49 in which the movable body 53 is accommodated, and is a refrigerant from the high pressure side to the low pressure side. Since the gas leakage is suppressed, it is possible to prevent a variation in the differential pressure due to the refrigerant gas leakage.
(3) Since the seal member 68 is a C-ring having a notch 68a, even if the discharge flange 46 and the movable body 53 forming the movable body accommodating portion 49 are made of different materials, the clearance C varies due to thermal expansion. The influence can be suppressed by the seal member 68 absorbing the fluctuation.
(4) A gap d shown in FIG. 4 is formed between the bottom surface of the annular groove 66 and the inner diameter surface of the seal member 68 facing the bottom surface, and the gap d is a clearance due to thermal expansion and contraction of the movable body 53. C variations can be absorbed as well.
(5) Since the friction between the seal member 68 and the inner wall surface of the movable body accommodating portion 49 is obtained, the elastic force of the coil spring 56 can be set weaker than before. For example, the downsizing of the coil spring 56 contributes to downsizing and weight reduction of the compressor.
(6) Since the seal member 68 absorbs the fluctuation of the clearance C, it is not necessary to form the accuracy of the inner diameter dimension of the movable body accommodating portion 49 more strictly than in the past, and the clearance C is within the range that can be absorbed by the seal member 68. You only have to set it.

(Second Embodiment)
Next, a compressor according to a second embodiment will be described with reference to FIG.
The second embodiment is an example in which a sealing member as a sliding contact member is formed in a spiral shape, and a spiral groove as a mounting groove corresponding to the sealing member is formed on the outer peripheral surface of the movable body.
Since the basic structure of the compressor of this embodiment is the same as that of the first embodiment, the description of the configuration common to the compressor uses the description of the first embodiment, and the common elements are denoted by reference numerals. Used in common.

As shown in FIG. 6, the movable body 73 of this embodiment has a cylindrical shape having an upper end small diameter portion 74 and a lower end large diameter portion 75.
The upper end small diameter portion 74 has a gap with the inner wall surface of the movable body accommodating portion 49, and a magnet 77 is embedded in the upper end small diameter portion 74.
A concave portion 75a is formed in the lower end large diameter portion 75, and a coil spring 56 is provided as a resilient means for pressing the movable body 73 upward in the concave portion 75a.
A perforated locking member 58 is attached to the inner wall surface of the movable body accommodating portion 49 near the low pressure space 48b.
The outer diameter of the lower end large diameter portion 75 substantially corresponds to the inner diameter of the movable body accommodating portion 49, and although not shown, the clearance between them is a clearance allowing the movable body 73 to slide within the movable body accommodating portion 49. It has become.

A spiral groove 78 having a U-shaped cross section is formed on the outer peripheral surface of the lower end large diameter portion 75, and a spiral seal member 79 is attached to the spiral groove 78.
The spiral seal member 79 is made of a rubber material.
In a state where the movable body 73 in which the seal member 79 is mounted in the spiral groove 78 is accommodated in the movable body accommodation portion 49, the seal member 79 generates an elastic force that expands toward the inner wall surface of the movable body accommodation portion 49.
Accordingly, a gap is formed between the bottom surface of the spiral groove 78 and the inner diameter surface of the seal member 79 facing the bottom surface.
This gap functions as a gap that similarly absorbs a variation in clearance due to thermal expansion and contraction of the movable body 53.
The spiral groove 78 has a substantially square cross-sectional shape of the seal member 79, and the seal member 79 is in surface contact with the inner wall surface of the movable body accommodating portion 49 and in surface contact with the spiral groove 78.
According to this embodiment, the same effect as the first embodiment can be expected.

(Third embodiment)
Next, a compressor according to a third embodiment will be described with reference to FIG.
The third embodiment is an example using a plurality of elastic members as sliding contact members.
Since the basic structure of the compressor of this embodiment is the same as that of the first embodiment, the description of the configuration common to the compressor uses the description of the first embodiment, and the common elements are denoted by reference numerals. Used in common.

As shown in FIG. 7, the movable body 83 of this embodiment has a cylindrical shape having an upper end small diameter portion 84 and a lower end large diameter portion 85.
The upper end small diameter portion 84 has a gap with the inner wall surface of the movable body accommodating portion 49, and a magnet 86 is embedded in the upper end small diameter portion 84.
A recess 85a is formed in the lower end large diameter portion 85, and a coil spring 56 is provided as a resilient means for pressing the movable body 83 upward in the recess 85a.
A perforated locking member 58 is attached to the inner wall surface of the movable body accommodating portion 49 near the low pressure space 48 b, and the locking member 58 prevents the movable body 83 and the coil spring 56 from coming off.
The outer diameter of the lower end large-diameter portion 85 substantially corresponds to the inner diameter of the movable body accommodating portion 49, and although not shown, the clearance between them is a clearance that allows the movable body 83 to slide within the movable body accommodating portion 49. ing.

Four vertical grooves 88 having a U-shaped cross section along the moving direction of the movable body 83 are formed on the outer peripheral surface of the lower end large diameter portion 85.
These vertical grooves 88 correspond to mounting grooves, and are arranged at positions that maintain an angle of 90 degrees with each other in the movable body 83. These vertical grooves 88 are elastic members 89 in a form substantially corresponding to the vertical grooves 88. Are installed respectively.
The elastic body 89 is formed of a rubber material, and is set to have a size such that the outer surface of the vertical groove 88 is in contact with the inner wall surface of the movable body housing portion 49.
According to this embodiment, there exists an effect similar to the effect (1) which 1st Embodiment has.

(Fourth embodiment)
Next, a compressor according to a fourth embodiment will be described with reference to FIG.
In the fourth embodiment, the seal member as the sliding contact member is a C-ring, but this is an example in which the cut of the C-ring is modified.
Since the basic structure of the compressor of this embodiment is the same as that of the first embodiment, the description of the configuration common to the compressor uses the description of the first embodiment, and the common elements are denoted by reference numerals. Used in common.

As shown in FIG. 5, the seal member 68 of the first embodiment has a cut 68 a formed in the vertical direction. Therefore, when the circumferential length of the seal member 68 is increased due to thermal expansion, the end of the seal member 68 is Clash with each other.
When the end portions of the seal member 68 are in contact with each other, further thermal expansion may cause the seal member 68 to expand excessively in the radial direction.
The sealing member 68 that expands excessively in the radial direction increases the frictional force with the discharge flange portion 46 and decreases the sliding performance of the movable body 53.
Therefore, in this embodiment, a device for preventing or suppressing excessive expansion of the seal member due to thermal expansion is elaborated.

As shown in FIG. 8A, a seal member 90 as a sliding contact member is attached to the annular groove 66 of the movable body 53 of this embodiment.
The seal member 90 of this embodiment is a C-ring having a cut 90a, and the cut 90a is formed to be inclined.
The seal member 90 is the same as the seal member 68 of the first embodiment in that the material is an elastic body and has a biasing force that spreads toward the inner wall surface of the movable body housing portion 49.
The inclination of the cut 90a in the seal member 90 is caused by shifting the end of the seal member 90 up and down as shown in FIG. 8B, even if the gap of the cut 90a is filled by thermal expansion. The seal member 90 functions to escape in the circumferential direction.
The end of the seal member 90 is displaced up and down and escapes in the circumferential direction, thereby preventing the seal member 90 from expanding in the radial direction.
According to this embodiment, since expansion of the seal member 90 in the radial direction can be prevented, an increase in frictional force between the seal member 90 and the discharge flange portion 46 can be prevented or suppressed.
In order to shift the end portion of the seal member 90 up and down to escape in the circumferential direction of the seal member 90, the cross-sectional width of the annular groove 66 is preferably set larger than the cross-sectional width of the seal member 90.

The present invention is not limited to the first to fourth embodiments described above. For example, various modifications can be made within the scope of the invention as follows.
○ In the above first to fourth embodiments, the sliding direction of the movable body is up and down. However, it is not necessarily limited to the up and down direction, and the discharge flange as the flange member is up and down, left and right, front and rear of the housing. It does not prevent it from being installed at any position. In this case, the sliding direction of the movable body may be set to a direction corresponding to the attachment position of the flange member, or the sliding direction of the movable body may be set regardless of the joining position of the discharge flange.
In the above first to fourth embodiments, the cross-sectional shape of the seal member as the slidable contact member is substantially rectangular, but the slidable contact member is, for example, a seal having an L-shaped cross section shown in FIG. Like the member 91, the sealing member 92 having a trapezoidal cross section shown in FIG. 9B, and the sealing member 93 having a substantially U-shaped cross section shown in FIG. Any sliding contact member having a free shape as long as it functions as a member can be freely selected.
In the above first to fourth embodiments, the throttle portion is interposed in the flange passage, and the detection sensor is a sensor that detects the differential pressure at two points upstream and downstream of the throttle portion in the flange passage. The detection sensor may be, for example, a check valve type sensor having a function as a check valve that opens and closes the flange passage in accordance with the fluid resistance in the flange passage.
In the above first to fourth embodiments, the flange member is made of metal. However, the flange member may be formed of the same resin material as that of the movable body. In this case, since the thermal expansion is the same for both, the C ring An O-ring seal member may be used instead of the seal member.
In the first embodiment, the capacity control valve is controlled based on the suction pressure of the first pressure detection passage. However, the capacity control valve is not limited to the suction pressure, A flow rate differential pressure control valve whose opening degree is adjusted based on the control signal and the differential pressure between the two pressure points of the two pressure detection passages may be used via the second pressure detection passage that is lower than the pressure of the pressure detection passage. Also, it may be an ON / OFF solenoid valve that controls the valve opening amount only by electromagnetic force.

It is a longitudinal section of the variable capacity type compressor concerning a 1st embodiment. It is an arrow line view of the AA line in FIG. It is sectional drawing which expands and shows the flow volume detection apparatus which concerns on 1st Embodiment. It is sectional drawing which expands and shows the principal part of the movable body which concerns on 1st Embodiment, and a sealing member. It is a perspective view of the seal member concerning a 1st embodiment. It is sectional drawing which expands and shows the movable body of the variable capacity type compressor which concerns on 2nd Embodiment. It is sectional drawing which expands and shows the movable body of the variable capacity type compressor which concerns on 3rd Embodiment. It is sectional drawing which expands and shows the movable body of the variable capacity type compressor which concerns on 4th Embodiment. It is principal part sectional drawing which shows another example of the sealing member as a sliding contact member.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Housing 12 Cylinder block 15 Crank chamber 16 Drive shaft 22 Piston 27 Discharge chamber 46 Discharge flange 48a High pressure space 48b Low pressure space 49 Movable body accommodating part 53, 73 Movable body 54, 74 Upper end small diameter part 55, 75 Lower end large diameter part 56 Coil Spring 57, 77 Magnet 59 Mounting member 60 Magnetic sensor 66 Annular groove (as mounting groove)
68, 79, 90 to 93 Seal member (as a sliding contact member)
68a, 90a Notch 78 Spiral groove (as mounting groove)
88 Longitudinal groove (as mounting groove)
89 Elastic member (as sliding contact member)
C clearance d gap

Claims (4)

A refrigerant passage including a suction pressure region and a discharge pressure region is formed in a housing having a cylinder bore and a crank chamber, a piston is accommodated in the cylinder bore, a swash plate is accommodated in the crank chamber, and is joined to the housing. A flange member is provided, the flange member forms a flange passage between the external refrigerant circuit and the refrigerant passage in the housing, is movable according to the flow rate of the refrigerant gas in the flange passage, and has a magnet. And in a variable capacity compressor having a detection sensor for detecting the magnetic flux density of the magnet,
The flange member has a movable body accommodating portion that accommodates the movable body,
The variable capacity compressor according to claim 1, wherein the movable body includes a sliding contact member that is in sliding contact with an inner wall surface of the movable body accommodating portion. The movable body has an outer peripheral surface having a circular cross section, the movable body housing portion has an inner wall surface having a circular cross section corresponding to the outer peripheral surface, and a mounting groove for mounting the sliding contact member is formed on the outer peripheral surface. The variable capacity compressor according to claim 1, wherein the compressor is formed. The mounting groove is an annular groove, the sliding contact member is a C-ring formed of an elastic material, and the sliding contact member extends from the annular groove to an inner wall surface of the movable body accommodating portion. 3. The variable capacity compressor according to claim 2, further comprising an urging force for urging the compressor. The variable capacity compressor according to any one of claims 1 to 3, wherein the movable body is pressed in one direction by an elastic means.

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