JPH02256892A - Variable delivery compressor - Google Patents

Abstract

PURPOSE:To adjust the intake rate of a compressor continuously variably and independent of the rotary speed of the rotor by disposing an oscillating mechanism for oscillating a first and a second semicylindrical members for expanding and contacting a cylinder space. CONSTITUTION:Semicylindrical members 23, 24 are constantly urged against cams 35, 36 with the pressure of a coolant gas compressed in a cylinder space 25 and with the centrifugal force of vanes. Therefore the semicylindrical members 23, 24 follow the rotation of the cams 35, 36, rotate within a housing 20, and expand or contract the volume of a cylinder space 25. When the intake rate of a compressor is adjusted to a minimum, a projection 232 enters a recess 201 formed in the housing 20 and a gap formed between the recess 201 and the projection 232 is reduced. As the intake rate increases, the gap between the recess 201 and the projection 232 increases. Even in the case a large intake rate is required, intake resistance does not increase.

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a compressor used in an air conditioner or the like, and particularly relates to a variable capacity compressor whose suction capacity can be adjusted as necessary.

(Prior Art) In recent years, with the spread of air conditioners, the demand for compressors has increased. In these air conditioners, it is necessary to increase the capacity of the compressor in order to shorten the time it takes for the indoor temperature to reach the set temperature.

However, after the indoor temperature reaches the set temperature, a large air conditioning capacity is not required, so a large capacity compressor has excessive capacity.

In order to solve these problems, a compressor has been proposed that has a structure in which the suction capacity of the compressor can be adjusted, and that reduces the suction capacity of the compressor after the indoor temperature reaches the set temperature. Publication No. 57-206789, etc.).

Referring to FIG. 9, a conventional variable displacement compressor disclosed in Japanese Patent Application Laid-Open No. 57-206789 will be described. A cylinder member 2 is inserted into a cylindrical housing I. A cylinder space 3 having an elliptical cross section is formed in the cylinder member 2 . A rotor 4 is rotatably disposed within the cylinder space 3. This rotor 4 has four vanes 5a, 5b, 5c, and 5d arranged as a tail.

The cylinder space 3 is divided into four spaces 3a, 3b, 3c, and 3d by vanes 5a, 5b, 5c, and 5d.

When the rotor 4 rotates clockwise (in the direction of the arrow in the figure), the volumes of the spaces 3a and 3c expand, and the volumes of the spaces 3b and 3d contract.

Suction ports 5a and 5b are opened in the spaces 3a and 3c. Therefore, as the volumes of the spaces 3a, 3c expand, the suction ports 6a, 6b allow refrigerant gas to flow into the spaces 3a, 3c. On the other hand, space 3b.

The refrigerant gas in 3C is compressed as the volumes of spaces 3b and 3d decrease, and is discharged from discharge lowers a and 7b.

A reed valve 8a8b is fixed to the discharge lowers a, 7b to prevent refrigerant gas from flowing backward from the discharge side flow paths 9a, 9b.

Further, the spaces 3b and 3d each have two adjustment ports 10a for adjusting the suction capacity of the compressor.

10b, 10c, and 10d are open.

The configurations of the adjustment ports 10a, 10b and the adjustment ports LOc, 10d are exactly the same, so in the following explanation, the adjustment ports 10a, 10b will be referred to as the adjustment ports 10a, 10b.
I will only explain about.

FIG. 10 shows a cross section of the adjustment ports 10a and 10b.

These adjustment ports 10a, 10b communicate with the suction ports 6a, 6b via a communication path 11. Adjustment ports 10a, 10b
Opening/closing valves 12a and 12b are inserted into the opening/closing valves 12a and 12b. The opening and closing valves 12a and 12b are controlled to open and close by switching the three-way valves 13a and 13b.

When the on-off valves 12a and 12b are both closed, the refrigerant gas is compressed from the time when the space 3b is separated from the suction port 6a by the vane 6a. Therefore, the suction capacity of the compressor is maximized. However, when the on-off valve 12a is opened, even if the volume of the space 3b decreases, the refrigerant gas continues to leak out to the suction port 6a through the communication passage 11 until the space 3b is separated from the adjustment port 10a by the vane 6a. , the suction capacity of the compressor decreases. In exactly the same way, when the on-off valve 12b is opened, the refrigerant gas leaks out until the space 3b is separated from the adjustment port 10b by the vane 6a, thereby further reducing the suction capacity of the compressor.

In this way, in the conventional device, the on-off valve 12a.

The suction capacity of the compressor is adjusted by opening and closing 12b and causing the refrigerant gas in the space 3b whose volume decreases to leak to the suction port 6a.

(Problem to be Solved by the Invention) However, in the conventional device described above, the on-off valve 12
The suction capacity of the compressor was adjusted by opening and closing ports a and 12b. Therefore, there was a problem that the inhalation capacity could only be adjusted in stages.

Therefore, the first technical problem of the present invention is to steplessly adjust the suction capacity of the compressor.

Further, in the conventional device described above, the space 3b whose volume decreases
The suction capacity of the compressor was adjusted by causing the refrigerant gas inside to leak through the communication port 11 to the suction port 6a. Therefore, when the rotational speed of the rotor 4 increases, the communication path 1
There was a problem in that the amount of refrigerant gas leaking out through the compressor was reduced, and the suction capacity of the compressor was increased.

Therefore, the second technical problem of the present invention is to adjust the suction capacity of the compressor independently of the rotational speed of the rotor.

[Structure of the invention]

(Means for Solving the Problems) The technical means taken to achieve the first and second technical problems described above is to install a first semi-cylindrical member and a second semi-cylindrical member in a substantially cylindrical housing. A semi-cylindrical member is swingably supported,
A cylinder space is formed by the first semi-cylindrical member and the second semi-cylindrical member, and the first semi-cylindrical member and the second semi-cylindrical member are rocked in order to expand or contract the cylinder space. This is because a swinging mechanism has been installed.

According to the above-mentioned technical means, the cylinder space is formed by the first semi-cylindrical member and the second semi-cylindrical member. Therefore, by driving the swing mechanism to increase the volume of the cylinder space, the amount of refrigerant gas filled in the cylinder space increases, and the suction capacity of the compressor increases. Conversely, if the rocking mechanism is driven to reduce the volume of the cylinder space, the amount of refrigerant gas filled in the cylinder space will be reduced, and the suction capacity of the compressor will be reduced.

In this way, according to the above-mentioned technical means, the volume of the cylinder space can be continuously adjusted by adjusting the amount of rocking of the first semi-cylindrical member and the second semi-cylindrical member. Therefore, the suction capacity of the compressor can be adjusted steplessly, and the first technical object is achieved.

Further, according to the above-mentioned technical means, the suction capacity of the compressor is adjusted by changing the volume of the cylinder space. Therefore, there is no communication path for leaking refrigerant gas. Therefore, the suction capacity of the compressor can be adjusted independently of the rotational speed of the rotor, and the second technical object is achieved.

(Embodiment) Hereinafter, a preferred embodiment to which the present invention is applied will be described with reference to the accompanying drawings.

The configuration of the apparatus of this embodiment will be described below with reference to FIGS. 1M and 2. FIG. 1 is a sectional view of a compressor depicting the apparatus of this embodiment, and is a sectional view taken along line BB in FIG. Also, the second
The figures are a sectional view taken along line 8-Δ in FIG. 1, FIG. 3 is a sectional view taken along line CC in FIG. 1, and FIG. 4 is a sectional view taken along line DD in FIG.

A front side plate 21 and a rear side plate 22 are fixed to the cylindrical housing 20 in an airtight manner. Furthermore, a front end plate 28 is airtightly fixed to the front side plate 21. A suction side passage 333 is formed between the front side plate 21 and the front end plate 28. Further, a rear end plate 29 is airtightly fixed to the rear side plays 1 and 22. A discharge pressure chamber 34 is formed between the rear side plate 22 and the rear end plate 29.

Inside the housing 20, a pair of semi-cylindrical members 23.
24 are arranged. The semi-cylindrical members 23 and 24 are exactly the same member.

A suction port 231 is opened in the semi-cylindrical member 23 . As shown in FIG. 3, the suction port 231 is opened in a protrusion 232 formed on the free end side of the semi-cylindrical member 23. As shown in FIG. The housing 20 has a recess 2 that engages with the protrusion 232.
01 is formed. The gap between the free end side of the semi-cylindrical member 23 and the housing 20 and the suction port 231 communicate the suction pressure chamber 331 and the cylinder space 25 .

Further, the semi-cylindrical member 23 has three discharge ports 233.2.
34,235 are open. As shown in FIG. 4, the discharge ports 233, 234, and 235 are opened on the supporting end side of the semicylindrical member 23.

Further, a protrusion 239 is formed on the support end side of the semi-cylindrical member 23. Furthermore, the housing 20 has a protrusion 23
A recess 203 is formed in which 9 engages. Projection 239
By engaging the recess 203 with the semi-cylindrical member 23
The discontinuity between the housing 20 and the housing 20 is
6.267.268 can pass smoothly.

As shown in FIG. 2, each discharge port 233°, 234.
Reed valves 301, 302, and 303 are fixed to 235. The discharge ports 233 , 234 , 235 communicate with a discharge passage 236 .

Shaft portions 237 and 238 are formed at both ends of the discharge side passage 236. The shaft portion 237 is the front side plate 21
It is rotatably fitted into a recessed portion 211 formed in . Further, the shaft portion 238 is rotatably fitted into an opening 211 formed in the rear side plate 22. Therefore, the semi-cylindrical member 23 can rotate within the housing 20 with the discharge side passage 236 as the rotation axis.

The semi-cylindrical member 24 is the same member as the semi-cylindrical member 23. Therefore, the description related to the semi-cylindrical member 24 will be briefly described. A suction port 241 is also provided in the semi-cylindrical member 24.
is opened. The suction port 231 is opened in a protrusion 242 formed at the free end of the semi-cylindrical member 23. The housing 20 is formed with a recess 202 that engages with the protrusion 232 .

The semi-cylindrical member 24 also has three discharge ports 243.2.
44 and 245 are opened, and each discharge port 243,
244, 245, reed valves 311, 312, 313
is fixed. The discharge ports 243, 244, 245 communicate with a discharge side passage 246.

Shaft portions 247 and 248 are formed at both ends of the discharge side passage 246. The shaft portion 247 is the front side plate 21
The shaft portion 248 is rotatably fitted into the recessed portion 212 formed in the rear side plate 22.
21 so as to be rotatable. Therefore, the semi-cylindrical member 24 rotates around the housing 2 with the discharge side passage 246 as the rotation axis.
It can rotate within 0.

The semi-cylindrical member 23 is connected to the housing 20. The space surrounded by the front side plate 21 and the rear side plate 22 is divided into two, a suction pressure chamber 331 and a cylinder space 25.

The front side plate 21 has four communication ports 213.
, 214, 215, and 216 are opened. These communication ports 213, 214, 215° 216 are connected to the suction pressure chamber 33.
1,332 and the suction side passage 333 are communicated with each other. The suction pressure chambers 331 and 332 communicate with each other via a suction side passage 332.

The cylinder space 25 is formed by the front side plate 21, the rear side plate 22 and the semi-cylindrical members 23,24. A cylindrical rotor 26 is inserted into the cylinder space 25 .

The rotor 26 is fixed to a drive shaft 27. This drive shaft 27
are front end plate 28 and rear side plate 2
The rotor 26 and the drive shaft 27 rotate together.

In order to maintain airtightness between the drive shaft 27 and the front end plate 28, a seal 32 is inserted between the drive shaft 27 and the front end plate 28.

The rotor 26 has four grooves 261, 262, 263.2.
64 is formed. Each groove 261°262.26
3.264 includes vanes 265°266.267.
268 is fitted. The cylinder space 25 is divided into a plurality of working chambers 251, 252, 253, 254, 255, 256 by vanes 265, 266, 267° 268.

Each groove 261, 262, 263, 264 has an oil passage (
(not shown) through which lubricating oil is directed, and the pressure of the lubricating oil forces the vanes 265, 266, 267, 268 towards the semi-cylindrical member 23, 24.

When the rotor 26 rotates in the direction of the arrow shown in FIG.
31, 241 and the recesses 201 and 202. The refrigerant gas sucked into the cylinder space 25 is discharged through the discharge ports 233, 234, 235, 243, 244,
245 and flows out to the discharge side passages 236, 246.

The refrigerant gas is then discharged to the discharge side passages 236 and 246 and is discharged to the outside of the compressor through the discharge pressure chamber 34.

The volume of refrigerant gas discharged from the compressor when the rotor 26 rotates is determined by the semi-cylindrical members 23, 24 and the housing 20.
It can be adjusted by rotating it within.

Hereinafter, a mechanism for adjusting the suction capacity of the compressor will be explained with reference to FIG. FIG. 5 is a sectional view taken along the line EE in FIG.

A cam 35.36 rests on the semi-cylindrical member 23.24. The semi-cylindrical members 23,24 are attached to these cams 35.
36. The cams 35, 36 are each formed integrally with a camshaft 37, 38.

Camshaft 37°38 is front side plate 21
and is rotatably supported by the rear end plate 29. Seals 39, 40 are also arranged between the camshafts 37, 38 and the rear side plate 22.

Gears 41 and 42 are fixed to one end of the camshaft 37 and 38. These gears 41, 42 mesh with a drive gear 43. The drive gear 43 is fixed to the gear shaft 44 and rotates together with the gear shaft 44. A worm wheel 45 is fixed to the gear shaft 44. A worm gear 46 is engaged with the worm wheel 44 . Worm gear 46 is rotated by motor 47. Therefore, when the motor 47 rotates, the cams 35,36 rotate.

The semi-cylindrical member 23.24 is always urged toward the cam 35.36 by the pressure of the refrigerant gas compressed in the cylinder space 25 and the Hoene centrifugal force. Accordingly, the semi-cylindrical member 23.24 rotates within the housing 20 following the rotation of the cam 35.36, expanding or contracting the volume of the cylinder space 25.

When the cams 35, 36 are in the state shown in FIG. 1, the volume of the cylinder space 25 is at its maximum, and the suction capacity of the compressor is at its maximum. When the cam 35.degree. 36 rotates from this state to the state shown in FIG. 6, the volume of the cylinder space 25 becomes minimum, and the suction capacity of the compressor becomes minimum.

FIG. 7 shows a sectional view taken along line FF in FIG. 6. When the suction capacity of the compressor is adjusted to the minimum, the protrusion 232 enters the recess 201 formed in the housing 20,
The gap formed between the recess 201 and the protrusion 232 becomes smaller, but as the suction capacity increases, the gap between the recess 201 and the protrusion 232 increases, and even when a large suction capacity is required, suction resistance is reduced. does not increase. The discharge port is also shaped to prevent overcompression from occurring.

FIG. 8 shows a sectional view taken along line GC in FIG. 6. When the suction capacity of the compressor is adjusted to a minimum, the housing 20
The protrusion 239 fits into the recess 203 formed in the recess 203 . At this time, parts of the discharge ports 233, 234 and 235 are covered by the housing 20, so the discharge ports 233, 234, 2
35 membrane area decreases. Therefore, refrigerant gas is difficult to be discharged to the discharge side passage 236, and the discharge capacity of the compressor is further reduced.

According to the apparatus of this embodiment described above, the cylinder space 25
Since the volume of the rotor 26 changes, the suction capacity of the compressor changes
can be controlled independently of the rotation speed.

Also, depending on the position of the cams 35 and 36, the cylinder space 25
Since the volume of the compressor can be adjusted continuously, the suction capacity of the compressor can be adjusted steplessly.

Further, when the suction capacity is large, the membrane area of the suction port and the discharge port becomes large, and when the suction capacity is small, the membrane area of the suction port and the discharge port becomes small. Therefore, even if the suction capacity changes, the compressor can smoothly perform suction Q compression Q discharge operations.

〔Effect of the invention〕

According to the present invention, the volume of the cylinder space can be continuously adjusted by adjusting the amount of rocking of the first semi-cylindrical member and the second semi-cylindrical member. Therefore, the suction capacity of the compressor can be adjusted steplessly.

Further, according to the present invention, the suction capacity of the compressor is adjusted by changing the volume of the cylinder space, and there is no communication path for leaking refrigerant gas. Therefore, the suction capacity of the compressor can be adjusted independently of the rotational speed of the rotor.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a compressor depicting a preferred embodiment of the present invention. Figure 2 is a sectional view taken along line A-A of the first cabinet. FIG. 3 is a sectional view taken along line CC in FIG. FIG. 4 is a sectional view taken along the line [)-D in FIG. 1. FIG. 5 is a sectional view taken along the line EE in FIG. FIG. 6 is a sectional view of the compressor corresponding to No. 1M, excluding the state in which the suction capacity is adjusted to the minimum. FIG. 7 is a sectional view taken along line FF in FIG. 6. FIG. 8 is a GC sectional view of the 6M. FIG. 9 and FIG. 1O are cross-sectional views depicting a conventional compressor. 20...Housing (housing), 201, 202
．． 203... recess, 21... front side plate, 21L 212.
... Recessed part, 213, 214.215.216 ... Communication port, 22 ... Rear side plate, 221.222
... opening, 23 ... semi-cylindrical member (first semi-cylindrical member), 231 ... suction port (first suction port), 23
2...Protrusion, 233, 234.235...Discharge port (
first discharge port), 236...discharge side passage, 237.2
38... Shaft portion, 239... Protrusion, 24... Semi-cylindrical member (second semi-cylindrical member), 241... Inlet (
second suction port), 242... protrusion, 243, 244.
245...Discharge port (second discharge port), 246...Discharge side passage, 247.248...Shaft portion, 249...Protrusion, 25...Cylinder space (cylinder space), 26 ...
Rotor (rotor), 261.262.263.264
...Groove, 265, 266, 267, 268... Vane (vane), 27... Drive shaft (drive shaft), 28... Front end plate, 29... Rear end plate, 301, 302. 303...Reed valve, 311, 3
12.313... Reed valve, 32... Seal, 33
1.332... Suction pressure chamber, 333... Suction side passage,
34...Discharge pressure chamber, 35, 36...Cam (swing mechanism), 37, 38...Camshaft (swing mechanism), 39, 4
0... Seal, 41.42... Gear (swing mechanism),
43... Drive gear (swing mechanism), 44... Gear shaft (swing mechanism), 45... Worm wheel (
Swinging mechanism), 46... Worm gear (swinging mechanism), 4
7...Motor (oscillating mechanism).

Claims (1)

[Scope of Claims] A substantially cylindrical housing; a first semi-cylindrical member that is pivotally supported with respect to the housing and swings within the housing; and an opening in the first semi-cylindrical member. a first suction port, a first ejection port, and a second semi-cylindrical member that is pivotally supported relative to the housing, swings within the housing, and forms a cylinder space together with the first semi-cylindrical member. a second inlet and a second outlet opened in the second semi-cylindrical member; a swinging mechanism for swinging the first and second semi-cylindrical members; and the housing. a rotor that rotates integrally with a drive shaft that is rotatably supported by the cylinder and is rotatably disposed within the cylinder space; and a rotor that rotates integrally with the rotor and divides the cylinder space into a plurality of working chambers. A variable displacement compressor comprising a plurality of vanes and.