[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

JP6184837B2 - Screw compressor - Google Patents

Screw compressor Download PDF

Info

Publication number
JP6184837B2
JP6184837B2 JP2013225764A JP2013225764A JP6184837B2 JP 6184837 B2 JP6184837 B2 JP 6184837B2 JP 2013225764 A JP2013225764 A JP 2013225764A JP 2013225764 A JP2013225764 A JP 2013225764A JP 6184837 B2 JP6184837 B2 JP 6184837B2
Authority
JP
Japan
Prior art keywords
rotor
tooth
compression chamber
discharge port
end surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2013225764A
Other languages
Japanese (ja)
Other versions
JP2015086782A (en
Inventor
紘太郎 千葉
紘太郎 千葉
土屋　豪
豪 土屋
太田　広志
広志 太田
正彦 高野
正彦 高野
茂幸 頼金
茂幸 頼金
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Industrial Equipment Systems Co Ltd
Original Assignee
Hitachi Industrial Equipment Systems Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Industrial Equipment Systems Co Ltd filed Critical Hitachi Industrial Equipment Systems Co Ltd
Priority to JP2013225764A priority Critical patent/JP6184837B2/en
Priority to CN201410412367.4A priority patent/CN104595185B/en
Publication of JP2015086782A publication Critical patent/JP2015086782A/en
Application granted granted Critical
Publication of JP6184837B2 publication Critical patent/JP6184837B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、スクリュー圧縮機に関する。   The present invention relates to a screw compressor.

一対のロータ（雄ロータと雌ロータ）が噛み合って回転して作動流体を圧縮するスクリュー圧縮機は、潤滑や冷却を目的として、２つのロータに作動油が供給される。供給された作動油は、圧縮される作動流体とともに吐出端面まで移動して吐出口から排出される。このとき、吐出口が作動油によって一時的に閉塞されると、吐出口からの作動流体の吐出が妨げられる。そして、作動流体の圧力が一時的に高くなる。
このように作動流体の圧力が一時的に高くなると、２つのロータなどの構造物に高圧が作用するため構造物の寿命が短くなるなどの問題が生じる。 In a screw compressor in which a pair of rotors (male rotor and female rotor) are engaged and rotated to compress a working fluid, hydraulic oil is supplied to the two rotors for the purpose of lubrication and cooling. The supplied hydraulic oil moves to the discharge end surface together with the compressed working fluid and is discharged from the discharge port. At this time, if the discharge port is temporarily blocked by the hydraulic oil, discharge of the working fluid from the discharge port is hindered. And the pressure of a working fluid becomes high temporarily.
As described above, when the pressure of the working fluid temporarily increases, a high pressure acts on a structure such as two rotors, which causes a problem that the life of the structure is shortened.

この問題を解決するための技術として特許文献１には、「ベアリングヘッドケーシングの吐出端面上の吐出ポート部に隣接し、かつ流体の閉じ込みが形成される部分に、閉じ込み流体を一旦収容することのできる凹所を形成するか、ベアリングヘッドケーシングの吐出端面に接するオスロータ又はメスロータの吐出端面上の流体の閉じ込みが形成される部分に、閉じ込み流体を一旦収容することのできる凹所を形成する」と記載されている（問題点を解決するための手段の項参照）。
特許文献１に記載されるスクリュー式圧縮機は、吐出端面まで移動した作動油（閉じ込み流体）を一旦収容する凹所を設けて作動油による吐出口（吐出ポート）の閉塞を抑制するように構成されている。 As a technique for solving this problem, Patent Document 1 discloses that “a confining fluid is temporarily accommodated in a portion adjacent to a discharge port portion on a discharge end surface of a bearing head casing and where a fluid confinement is formed. A recess capable of temporarily containing the confining fluid in a portion where the fluid confinement is formed on the discharge end surface of the male rotor or the female rotor in contact with the discharge end surface of the bearing head casing. (Refer to the section on means for solving the problem).
The screw-type compressor described in Patent Document 1 is provided with a recess that temporarily stores hydraulic oil (confining fluid) that has moved to the discharge end face so as to suppress blockage of the discharge port (discharge port) due to the hydraulic oil. It is configured.

特開昭６３−３６０８３号公報Japanese Unexamined Patent Publication No. Sho 63-36083

特許文献１に記載されるスクリュー式圧縮機のように、２つのロータの少なくとも一方に凹所が形成される場合、この凹所は、ロータの吐出端面側の端面において互いに噛み合う部位に形成される。したがって、噛み合う２つのロータが回転すると、それぞれのロータの吐出端面側の端面で、隣接して形成されている螺旋状の溝（歯溝）が凹所を介して連通する場合がある。   When a recess is formed in at least one of the two rotors as in the screw compressor described in Patent Document 1, the recess is formed in a portion that meshes with each other on the end surface on the discharge end surface side of the rotor. . Therefore, when two meshing rotors rotate, adjacent spiral grooves (tooth grooves) may be communicated with each other through the recesses on the end surfaces on the discharge end surface side of the respective rotors.

作動室内に２つのロータを有するスクリュー圧縮機は、一方のロータ（雌ロータ）の歯溝に他方のロータ（雄ロータ）の歯部が噛み合って形成される空間に、作動流体を圧縮する圧縮室が形成される。また、雌ロータにおいて圧縮室となる歯溝に隣接する歯溝は、雄雄ロータおよび雌ロータを収容する作動室に連通する。圧縮室は圧縮された作動流体が存在する高圧の空間であり、作動室は圧縮途中の作動流体が存在する低圧の空間である。したがって、隣接して形成される歯溝が連通すると高圧の圧縮室と低圧の作動室が連通する。そして、圧縮室で圧縮された高圧の作動流体の一部が低圧の作動室に流入する。このため、圧縮された作動流体の一部が消失することになってロスが生じる。   A screw compressor having two rotors in a working chamber is a compression chamber that compresses a working fluid in a space formed by meshing a tooth portion of the other rotor (male rotor) with a tooth groove of one rotor (female rotor). Is formed. In addition, the tooth gap adjacent to the tooth groove serving as the compression chamber in the female rotor communicates with the working chamber that houses the male and female rotors and the female rotor. The compression chamber is a high-pressure space where compressed working fluid exists, and the working chamber is a low-pressure space where working fluid during compression exists. Therefore, when the adjacent tooth gaps communicate with each other, the high pressure compression chamber and the low pressure working chamber communicate with each other. A part of the high-pressure working fluid compressed in the compression chamber flows into the low-pressure working chamber. For this reason, a part of the compressed working fluid disappears and loss occurs.

そこで本発明は、圧縮された作動流体の消失を抑制可能で、吐出時の圧力上昇を抑制可能な構造のスクリュー圧縮機を提供することを課題とする。   Then, this invention makes it a subject to provide the screw compressor of the structure which can suppress the loss | disappearance of the compressed working fluid and can suppress the pressure rise at the time of discharge.

前記課題を解決するため本発明は、ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、前記第１ロータの歯部に、軸方向端面が凹んだ第１凹部が形成され、前記第１凹部は前記第１ロータの歯部の歯先に形成される第１開口部で前記作動室または前記圧縮室と連通し、前記第１開口部は、前記圧縮室が消滅したときに前記第１ロータの歯部の歯先と前記第２ロータの歯溝の歯底が重なりあう位置に開口し、前記第１凹部において前記第１開口部を臨む底面の法線は、前記第１ロータの回転軸の軸線方向の成分が、軸方向端面に向かい合う前記作動室内の端面の方向を向くことを特徴とする。 In order to solve the above problems, the present invention provides a first rotor and a second rotor that mesh with each other in a working chamber in a casing and rotate to compress a working fluid, and axial end surfaces of the first rotor and the second rotor. A discharge port that opens to an end face of the working chamber facing each other, and the working fluid is accompanied by a reduction in a compression chamber formed in a tooth groove of the second rotor meshed with a tooth portion of the first rotor. After being compressed, it is discharged to the outside of the casing through the discharge port provided so as to communicate with the compression chamber, and the compression chamber is reduced until it disappears to discharge the working fluid. A tooth portion of one rotor is formed with a first recess having a recessed end surface in the axial direction, and the first recess is a first opening formed at a tooth tip of the tooth portion of the first rotor, and the working chamber or the compression Communicating with the chamber, the first opening The opening opens at a position where the tooth tip of the tooth portion of the first rotor and the tooth bottom of the tooth space of the second rotor overlap when the compression chamber disappears, and the first opening portion in the first recess The normal line of the bottom surface facing is characterized in that the component in the axial direction of the rotation shaft of the first rotor faces the direction of the end surface in the working chamber facing the end surface in the axial direction .

本発明によると、圧縮された作動流体の消失を抑制可能で、吐出時の圧力上昇を抑制可能な構造のスクリュー圧縮機を提供できる。   ADVANTAGE OF THE INVENTION According to this invention, the loss | disappearance of the compressed working fluid can be suppressed and the screw compressor of the structure which can suppress the pressure rise at the time of discharge can be provided.

スクリュー圧縮機の圧縮機本体の構成を示す断面図である。It is sectional drawing which shows the structure of the compressor main body of a screw compressor. 吐出端面の側から従来形状の第１ロータと第２ロータを見た図である。It is the figure which looked at the 1st rotor and the 2nd rotor of the conventional shape from the discharge end face side. 圧縮室における圧力の変化を示すグラフである。It is a graph which shows the change of the pressure in a compression chamber. （ａ）は、第１ロータの歯部に形成される油分収容部を示す図、（ｂ）は、油分収容部の斜視図である。(A) is a figure which shows the oil content accommodating part formed in the tooth | gear part of a 1st rotor, (b) is a perspective view of an oil content accommodating part. 圧縮室が消滅した状態を示す図である。It is a figure which shows the state which the compression chamber disappeared. 第１ロータの歯部にかき集められる作動油が油分収容部に流れ込む状態を示す図である。It is a figure which shows the state in which the hydraulic oil collected by the tooth | gear part of a 1st rotor flows in into an oil-component storage part. 図６におけるＳｅｃ１−Ｓｅｃ１での断面図である。It is sectional drawing in Sec1-Sec1 in FIG. （ａ）は、実施例２の油分収容部を示す図、（ｂ）は、油分収容部の斜視図である。(A) is a figure which shows the oil content accommodating part of Example 2, (b) is a perspective view of an oil content accommodating part.

以下、適宜図を参照して本発明の実施例を詳細に説明する。   Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate.

図１は、本発明の実施例１に係るスクリュー圧縮機の構成を示す断面図である。また、図２は、吐出端面の側から従来形状の第１ロータと第２ロータを見た図、図３は、圧縮室における圧力の変化を示すグラフである。また、図４の（ａ）は、第１ロータの歯部に形成される油分収容部を示す図、（ｂ）は、油分収容部の斜視図である。また、図５は、圧縮室が消滅した状態を示す図である。   1 is a cross-sectional view illustrating a configuration of a screw compressor according to Embodiment 1 of the present invention. FIG. 2 is a view of the first rotor and the second rotor having a conventional shape as viewed from the discharge end face side, and FIG. 3 is a graph showing a change in pressure in the compression chamber. FIG. 4A is a view showing an oil storage portion formed in the tooth portion of the first rotor, and FIG. 4B is a perspective view of the oil storage portion. FIG. 5 is a diagram showing a state in which the compression chamber has disappeared.

実施例１のスクリュー圧縮機１は、図１，図２に示すように、互いに噛み合って回転する第１ロータ１１（雄ロータ）と第２ロータ２０（雌ロータ）で作動流体を圧縮する。なお、図２に示すように、第１ロータ１１の回転方向Ｒｏｔ１と、第２ロータ２０の回転方向Ｒｏｔ２は、互いに逆方向になる。   1 and 2, the screw compressor 1 according to the first embodiment compresses the working fluid with a first rotor 11 (male rotor) and a second rotor 20 (female rotor) that mesh with each other and rotate. 2, the rotation direction Rot1 of the first rotor 11 and the rotation direction Rot2 of the second rotor 20 are opposite to each other.

第１ロータ１１と第２ロータ２０は、ケーシング１２の中空部として形成される作動室１３内に収納される。また、第１ロータ１１の回転軸１０ａが作動室１３を貫通するように備わっている。そして、回転軸１０ａの軸線方向の作動室１３の両端には、軸受室１５ａ，１５ｂが形成される。軸受室１５ａ，１５ｂには、回転軸１０ａを両端側で支持する軸受１４ａ，１４ｂが取り付けられる。なお、第２ロータ２０も同様に構成され、その回転軸１０ｂは、軸受室１５ａ，１５ｂに取り付けられる軸受（図示せず）で支持される。   The first rotor 11 and the second rotor 20 are accommodated in a working chamber 13 formed as a hollow portion of the casing 12. Further, the rotary shaft 10 a of the first rotor 11 is provided so as to penetrate the working chamber 13. Bearing chambers 15a and 15b are formed at both ends of the working chamber 13 in the axial direction of the rotating shaft 10a. Bearings 14a and 14b that support the rotary shaft 10a at both ends are attached to the bearing chambers 15a and 15b. The second rotor 20 is configured in the same manner, and the rotating shaft 10b is supported by a bearing (not shown) attached to the bearing chambers 15a and 15b.

ケーシング１２には、吸込口１６ａと吐出口１６ｂが形成される。吸込口１６ａは、圧縮する作動流体（実施例１では空気Ａｉｒとする）を作動室１３に取り込む。吐出口１６ｂは、圧縮された空気Ａｉｒを作動室１３から吐出する。そして、吸込口１６ａから吸い込まれた空気Ａｉｒが第１ロータ１１と第２ロータ２０の回転で圧縮されて吐出口１６ｂからケーシング１２の外部に吐出される。なお、作動室１３の端面を形成して吐出口１６ｂが開口する面を吐出端面１３ａとする。また、第１ロータ１１と第２ロータ２０において吐出端面１３ａに向かい合う端面を軸方向端面１１ｃ，２０ｃとする。また、第１ロータ１１と第２ロータ２０が噛み合う空間が圧縮室３０になる。   The casing 12 is formed with a suction port 16a and a discharge port 16b. The suction port 16a takes into the working chamber 13 a working fluid to be compressed (air Air in the first embodiment). The discharge port 16b discharges the compressed air Air from the working chamber 13. The air Air sucked from the suction port 16 a is compressed by the rotation of the first rotor 11 and the second rotor 20 and discharged from the discharge port 16 b to the outside of the casing 12. A surface on which the end surface of the working chamber 13 is formed and the discharge port 16b is opened is referred to as a discharge end surface 13a. Moreover, let the end surface which faces the discharge end surface 13a in the 1st rotor 11 and the 2nd rotor 20 be the axial direction end surfaces 11c and 20c. Further, the space where the first rotor 11 and the second rotor 20 are engaged becomes the compression chamber 30.

また、ケーシング１２には、作動室給油口１９が形成される。作動室給油口１９から作動室１３に作動油Ｏｉｌが供給される。スクリュー圧縮機１は、作動室１３で圧縮される空気Ａｉｒの冷却や、第１ロータ１１と第２ロータ２０の潤滑や、作動室１３に形成される隙間の密封のために作動室１３に作動油Ｏｉｌが供給される。そして、作動室１３に供給された作動油Ｏｉｌは圧縮された空気Ａｉｒとともに吐出口１６ｂから排出される。   The casing 12 is formed with a working chamber oil supply port 19. The hydraulic oil Oil is supplied to the working chamber 13 from the working chamber oil supply port 19. The screw compressor 1 operates in the working chamber 13 to cool the air Air compressed in the working chamber 13, lubricate the first rotor 11 and the second rotor 20, and seal a gap formed in the working chamber 13. Oil Oil is supplied. Then, the hydraulic oil Oil supplied to the working chamber 13 is discharged from the discharge port 16b together with the compressed air Air.

図１，図２に示すように、吐出口１６ｂは、作動室１３の吐出端面１３ａに開口する。吐出口１６ｂの形状は限定されるものではなく、第１ロータ１１と第２ロータ２０が噛み合って形成される圧縮室３０で圧縮された空気Ａｉｒが効率よく吐出される形状であればよい。   As shown in FIGS. 1 and 2, the discharge port 16 b opens in the discharge end surface 13 a of the working chamber 13. The shape of the discharge port 16b is not limited as long as the air Air compressed in the compression chamber 30 formed by the engagement of the first rotor 11 and the second rotor 20 is efficiently discharged.

圧縮室３０は、螺旋状に形成される第２ロータ２０の歯溝２０ａに、螺旋状に形成される第１ロータ１１の歯部１１ｂが噛み合って形成される。第１ロータ１１および第２ロータ２０の歯溝１１ａ，２０ａは、それぞれ螺旋状の歯部１１ｂ，２０ｂの間に形成される。図２の符号１１ｂ１は、歯部１１ｂの歯先であり、符号２０ａ１は、歯溝２０ａの歯底である。
なお、第１ロータ１１および第２ロータ２０には、それぞれ複数条の歯部１１ｂ，２０ｂが形成される。例えば、第２ロータ２０には６条の歯部２０ｂが形成され、第１ロータ１１には４条の歯部１１ｂが形成される。したがって、第２ロータ２０には６本の歯溝２０ａが形成され、第１ロータ１１には４本の歯溝１１ａが形成される。
そして、第１ロータ１１の歯部１１ｂが噛み合っている第２ロータ２０の歯溝２０ａが圧縮室３０になり、第２ロータ２０のその他の歯溝２０ａや第１ロータ１１の歯溝１１ａは作動室１３に連通する。このように、圧縮室３０は作動室１３から隔離された室になる。 The compression chamber 30 is formed by meshing the tooth portion 11b of the first rotor 11 formed in a spiral manner with the tooth groove 20a of the second rotor 20 formed in a spiral shape. The tooth grooves 11a and 20a of the first rotor 11 and the second rotor 20 are formed between the helical tooth portions 11b and 20b, respectively. 2 is a tooth tip of the tooth portion 11b, and 20a1 is a tooth bottom of the tooth gap 20a.
The first rotor 11 and the second rotor 20 have a plurality of teeth 11b and 20b, respectively. For example, six teeth 20 b are formed on the second rotor 20, and four teeth 11 b are formed on the first rotor 11. Accordingly, six tooth grooves 20 a are formed in the second rotor 20, and four tooth grooves 11 a are formed in the first rotor 11.
Then, the tooth groove 20a of the second rotor 20 meshed with the tooth portion 11b of the first rotor 11 becomes the compression chamber 30, and the other tooth grooves 20a of the second rotor 20 and the tooth grooves 11a of the first rotor 11 are operated. It communicates with the chamber 13. Thus, the compression chamber 30 is a chamber isolated from the working chamber 13.

吸込口１６ａ（図１参照）から吸い込まれた空気Ａｉｒは、作動室１３に取り込まれる。そして、第１ロータ１１と第２ロータ２０が回転して、第２ロータ２０の歯溝２０ａに第１ロータ１１の歯部１１ｂが噛み合うと、その歯溝２０ａが圧縮室３０になる。圧縮室３０の空気Ａｉｒは、第１ロータ１１と第２ロータ２０の回転にともなって吐出端面１３ａの側に送られながら圧縮される。そして、圧縮された空気Ａｉｒが吐出端面１３ａに開口している吐出口１６ｂから吐出する。   The air Air sucked from the suction port 16a (see FIG. 1) is taken into the working chamber 13. Then, when the first rotor 11 and the second rotor 20 rotate and the tooth portion 11 b of the first rotor 11 meshes with the tooth groove 20 a of the second rotor 20, the tooth groove 20 a becomes the compression chamber 30. The air Air in the compression chamber 30 is compressed while being sent to the discharge end face 13 a side as the first rotor 11 and the second rotor 20 rotate. Then, the compressed air Air is discharged from the discharge port 16b opened in the discharge end face 13a.

また、作動室給油口１９（図１参照）から作動室１３に供給された作動油Ｏｉｌは、回転する第１ロータ１１と第２ロータ２０の歯部１１ｂ，２０ｂによってかき集められて圧縮室３０に入り込む。圧縮室３０に入り込んだ作動油Ｏｉｌは、圧縮される空気Ａｉｒとともに吐出端面１３ａの側に送られて吐出口１６ｂから排出される。
このとき、図２に示すように作動油Ｏｉｌが吐出口１６ｂの一部を閉塞すると、空気Ａｉｌの吐出が妨げられる。そして、吐出されない空気Ａｉｒが圧縮室３０に溜まって高圧になる。その後、作動油Ｏｉｌが吐出口１６ｂから排出されるのにともなって空気Ａｉｒが吐出口１６ｂから吐出される。 Further, the hydraulic oil Oil supplied to the working chamber 13 from the working chamber oil supply port 19 (see FIG. 1) is collected by the rotating first rotor 11 and the tooth portions 11b and 20b of the second rotor 20 to the compression chamber 30. Get in. The hydraulic oil Oil that has entered the compression chamber 30 is sent to the discharge end face 13a together with the compressed air Air and is discharged from the discharge port 16b.
At this time, when the hydraulic oil Oil closes a part of the discharge port 16b as shown in FIG. 2, the discharge of the air Ail is hindered. And the air Air which is not discharged accumulates in the compression chamber 30, and becomes high pressure. Thereafter, the air Air is discharged from the discharge port 16b as the hydraulic oil Oil is discharged from the discharge port 16b.

従来、圧縮室３０の圧力（空気Ａｉｒの圧力）は、図３に示すグラフのように変化する。図３は、横軸が第１ロータ１１の回転角度θ、縦軸が圧縮室３０の圧力Ｐを示す。なお、第１ロータ１１の回転角度は、第１ロータ１１の歯部１１ｂが第２ロータ２０の歯溝２０ａに噛み合い始めた時点を起点（０度）とする。   Conventionally, the pressure in the compression chamber 30 (the pressure of the air Air) changes as shown in the graph of FIG. In FIG. 3, the horizontal axis represents the rotation angle θ of the first rotor 11, and the vertical axis represents the pressure P in the compression chamber 30. The rotation angle of the first rotor 11 is defined as a starting point (0 degree) when the tooth portion 11b of the first rotor 11 starts to mesh with the tooth groove 20a of the second rotor 20.

第１ロータ１１と第２ロータ２０が回転して第１ロータ１１の回転角度θが大きくなると、圧縮室３０での空気Ａｉｒの圧縮が進行して圧縮室３０の圧力Ｐが昇圧する（圧縮過程）。第１ロータ１１の回転角度θが所定の角度（θ＝「θ１」）に達すると、圧縮室３０が吐出口１６ｂと連通し、圧縮室３０の空気Ａｉｒが吐出口１６ｂから吐出される（吐出過程）。吐出過程で圧縮室３０の圧力Ｐは昇圧しない。なお、吐出過程における圧縮室３０の圧力が、スクリュー圧縮機１（図１参照）に設定される定格の吐出圧力「Ｐｓｔｄ」になる。   When the first rotor 11 and the second rotor 20 rotate and the rotation angle θ of the first rotor 11 increases, the compression of the air Air in the compression chamber 30 proceeds and the pressure P in the compression chamber 30 increases (the compression process). ). When the rotation angle θ of the first rotor 11 reaches a predetermined angle (θ = “θ1”), the compression chamber 30 communicates with the discharge port 16b, and the air Air in the compression chamber 30 is discharged from the discharge port 16b (discharge). process). The pressure P in the compression chamber 30 is not increased during the discharge process. The pressure in the compression chamber 30 during the discharge process becomes the rated discharge pressure “Pstd” set in the screw compressor 1 (see FIG. 1).

第１ロータ１１がさらに回転して回転角度θがある角度（θ＝「θ２」）になったとき、第１ロータ１１の歯部１１ｂと第２ロータ２０の歯部２０ｂでかき集められた作動油Ｏｉｌが吐出口１６ｂに到達して排出される。作動油Ｏｉｌが吐出口１６ｂから吐出される回転角度θの値「θ２」は定まった値ではない。   When the first rotor 11 further rotates and the rotation angle θ reaches an angle (θ = “θ2”), the hydraulic oil collected by the tooth portion 11b of the first rotor 11 and the tooth portion 20b of the second rotor 20 Oil reaches the discharge port 16b and is discharged. The value “θ2” of the rotation angle θ at which the hydraulic oil Oil is discharged from the discharge port 16b is not a fixed value.

作動油Ｏｉｌが吐出口１６ｂに到達すると圧縮室３０と連通している吐出口１６ｂの一部が作動油Ｏｉｌで閉塞され、空気Ａｉｒの吐出が妨げられる。これによって、空気Ａｉｒの吐出口１６ｂからの吐出に対する抵抗（吐出抵抗）が大きくなる。このため、圧縮室３０の圧力Ｐが吐出圧力「Ｐｓｔｄ」より昇圧する。その後、作動油Ｏｉｌが吐出口１６ｂから排出されると吐出口１６ｂが開放される。そして、吐出口１６ｂにおける空気Ａｉｒの吐出抵抗が小さくなり、圧縮室３０の圧力Ｐが低格の吐出圧力「Ｐｓｔｄ」まで降圧する。作動油Ｏｉｌが吐出口１６ｂを閉塞するのは一時的なものであり、圧縮室３０の圧力Ｐが昇圧するのも一時的なものになる。   When the hydraulic oil Oil reaches the discharge port 16b, a part of the discharge port 16b communicating with the compression chamber 30 is blocked with the hydraulic oil Oil, and the discharge of the air Air is prevented. As a result, the resistance (discharge resistance) to the discharge of the air Air from the discharge port 16b increases. For this reason, the pressure P in the compression chamber 30 is increased from the discharge pressure “Pstd”. Thereafter, when the hydraulic oil Oil is discharged from the discharge port 16b, the discharge port 16b is opened. Then, the discharge resistance of the air Air at the discharge port 16b is reduced, and the pressure P in the compression chamber 30 is lowered to the low discharge pressure “Pstd”. The hydraulic oil Oil blocks the discharge port 16b temporarily, and the pressure P in the compression chamber 30 increases temporarily.

このように、従来のスクリュー圧縮機１の吐出過程には、圧縮室３０の圧力Ｐが吐出圧力「Ｐｓｔｄ」よりも昇圧する瞬間がある。
そこで、図４の（ａ），（ｂ）に示すように、実施例１の第１ロータ１１には、軸方向端面１１ｃが凹んだ第１凹部（第１油分収容部２２）が設けられている。 Thus, in the discharge process of the conventional screw compressor 1, there is a moment when the pressure P in the compression chamber 30 is increased above the discharge pressure “Pstd”.
Therefore, as shown in FIGS. 4A and 4B, the first rotor 11 of the first embodiment is provided with a first recess (first oil container 22) in which the axial end surface 11 c is recessed. Yes.

第１油分収容部２２は、第１ロータ１１の歯部１１ｂの軸方向端面１１ｃが、回転軸１０ａ（図２参照）の軸方向に向かって凹んで形成される。また、第１油分収容部２２には、歯部１１ｂの歯先１１ｂ１に第１開口部２２ａが形成される。そして、第１ロータ１１の歯部１１ｂが第２ロータ２０の歯溝２０ａに噛み合って形成される圧縮部３０と第１油分収容部２２が第１開口部２２ａを介して連通する。また、第２ロータ２０の歯溝２０ａに噛み合わない歯部１１ｂの第１油分収容部２２は、第１開口部２２ａを介して作動室１３と連通する。なお、符号２２ｂは、第１開口部２２ａを臨む底面である。   The first oil storage portion 22 is formed such that the axial end surface 11c of the tooth portion 11b of the first rotor 11 is recessed toward the axial direction of the rotating shaft 10a (see FIG. 2). Moreover, the 1st opening part 22a is formed in the tooth | gear tip 11b1 of the tooth | gear part 11b in the 1st oil content accommodating part 22. FIG. And the compression part 30 formed by the tooth | gear part 11b of the 1st rotor 11 meshing with the tooth groove 20a of the 2nd rotor 20 and the 1st oil content accommodating part 22 are connected via the 1st opening part 22a. Further, the first oil component storage portion 22 of the tooth portion 11b that does not mesh with the tooth groove 20a of the second rotor 20 communicates with the working chamber 13 through the first opening portion 22a. In addition, the code | symbol 22b is a bottom face which faces the 1st opening part 22a.

第１開口部２２ａは、軸方向端面１１ｃ上で歯部１１ｂの輪郭線上にある２つの特異点Ｘ１，Ｘ２の間に形成される。ここでいう輪郭線は、第１ロータ１１の軸方向端面１１ｃにおける歯部１１ｂの輪郭線を示す。
また、特異点Ｘ１，Ｘ２は、第１ロータ１１と第２ロータ２０が噛み合って回転しているときに、第２ロータ２０の特異点Ｙ１，Ｙ２と重なる点である。特異点Ｘ１，Ｘ２、および特異点Ｙ１，Ｙ２は、下記のように設定される点である。 The first opening 22a is formed between two singular points X1 and X2 on the contour line of the tooth portion 11b on the axial end face 11c. The outline here refers to the outline of the tooth portion 11 b on the axial end surface 11 c of the first rotor 11.
Further, the singular points X1 and X2 are points that overlap with the singular points Y1 and Y2 of the second rotor 20 when the first rotor 11 and the second rotor 20 are engaged and rotating. The singular points X1 and X2 and the singular points Y1 and Y2 are points set as follows.

圧縮過程では、第１ロータ１１と第２ロータ２０の回転にともなって圧縮室３０は容積が減少する。また、吐出過程に移行しても第１ロータ１１と第２ロータ２０の回転にともなって圧縮室３０の容積は減少する。そして、圧縮室３０の容積が最小になった時点で吐出過程が終了する（吐出完了）。
実施例１のスクリュー圧縮機１（図１参照）は、吐出過程が終了する吐出完了時に、図５に示すように、圧縮室３０が消滅するように構成される。そして、このとき（すなわち、吐出完了時）、軸方向端面１１ｃ，２０ｃにおいて第１ロータ１１の歯部１１ｂと第２ロータ２０の歯溝２０ａが所定の幅で接触する。つまり、吐出完了時に、軸方向端面１１ｃ，２０ｃにおいて、第１ロータ１１の輪郭線の一部（歯先１１ｂ１）と第２ロータ２０の輪郭線の一部（歯底２０ａ１）が重なり合うように構成される。 In the compression process, the volume of the compression chamber 30 decreases as the first rotor 11 and the second rotor 20 rotate. Even if the process proceeds to the discharge process, the volume of the compression chamber 30 decreases as the first rotor 11 and the second rotor 20 rotate. Then, the discharge process ends when the volume of the compression chamber 30 becomes the minimum (discharge completion).
The screw compressor 1 according to the first embodiment (see FIG. 1) is configured such that the compression chamber 30 disappears as shown in FIG. At this time (that is, when the discharge is completed), the tooth portion 11b of the first rotor 11 and the tooth groove 20a of the second rotor 20 are in contact with each other with a predetermined width on the axial end surfaces 11c and 20c. In other words, when the discharge is completed, a part of the contour line of the first rotor 11 (tooth tip 11b1) and a part of the contour line of the second rotor 20 (tooth bottom 20a1) overlap each other on the axial end surfaces 11c and 20c. Is done.

そして、第１ロータ１１の歯部１１ｂ（歯先１１ｂ１）は、吐出完了時に特異点Ｘ１からＸ２までの間が、第２ロータ２０の歯溝２０ａ（歯底２０ａ１）の特異点Ｙ１からＹ２までの間と重なる。換言すると、第１ロータ１１の歯部１１ｂの輪郭線における特異点Ｘ１からＸ２までの間の曲率半径と、第２ロータ２０の歯溝２０ａの輪郭線における特異点Ｙ１からＹ２までの間の曲率半径が等しく構成される。第１ロータ１１の特異点Ｘ１，Ｘ２、および、第２ロータ２０の特異点Ｙ１，Ｙ２はこのように設定される点とする。   Then, the tooth portion 11b (tooth tip 11b1) of the first rotor 11 is between the singular points Y1 to Y2 of the tooth groove 20a (tooth bottom 20a1) of the second rotor 20 between the singular points X1 and X2 when the discharge is completed. It overlaps between. In other words, the curvature radius between the singular points X1 and X2 in the contour line of the tooth portion 11b of the first rotor 11 and the curvature between the singular points Y1 and Y2 in the contour line of the tooth groove 20a of the second rotor 20. Radius is configured equally. The singular points X1 and X2 of the first rotor 11 and the singular points Y1 and Y2 of the second rotor 20 are set as described above.

そして、第１開口部２２ａは、吐出完了時に圧縮室３０が消滅したときに、第１ロータ１１の歯部１１ｂ（歯先１１ｂ１）と、第２ロータ２０の歯溝２０ａ（歯底２０ａ１）が重なり合う位置に開口する。   The first opening 22a has a tooth portion 11b (tooth tip 11b1) of the first rotor 11 and a tooth groove 20a (tooth bottom 20a1) of the second rotor 20 when the compression chamber 30 disappears upon completion of discharge. Open at the overlapping position.

このような構成であれば、図４の（ａ）に示すように、圧縮過程や吐出過程で第１開口部２２ａは、圧縮室３０のみに開口する。また、図５に示すように、吐出完了時に圧縮室３０が消滅すると第１開口部２２ａは閉塞される。そして、吐出完了時から、さらに第１ロータ１１と第２ロータ２０が回転すると、第１開口部２２ａは作動室１３のみに開口する。   With such a configuration, as shown in FIG. 4A, the first opening 22 a opens only to the compression chamber 30 during the compression process and the discharge process. Further, as shown in FIG. 5, when the compression chamber 30 disappears when the discharge is completed, the first opening 22a is closed. When the first rotor 11 and the second rotor 20 are further rotated from the completion of the discharge, the first opening 22a opens only in the working chamber 13.

このように、実施例１の第１ロータ１１に設けられる第１開口部２２ａは、圧縮室３０のみに開口するか、作動室１３のみに開口するか、閉塞されるか、のいずれかになる。このため、第１開口部２２ａは、圧縮室３０と作動室１３の両方に同時に開口することがない。したがって、圧縮室３０と作動室１３が第１油分収容部２２を介して連通することがない。よって、圧縮室３０で圧縮された高圧の空気Ａｉｒが第１油分収容部２２を流通して作動室１３に流れ込まないので、圧縮された空気Ａｉｒは消失することなく吐出口１６ｂから吐出される。つまり、圧縮された空気Ａｉｒの消失を抑制できる。   As described above, the first opening 22a provided in the first rotor 11 of the first embodiment is either opened only to the compression chamber 30, opened only to the working chamber 13, or is closed. . For this reason, the 1st opening part 22a does not open to both the compression chamber 30 and the working chamber 13 simultaneously. Therefore, the compression chamber 30 and the working chamber 13 do not communicate with each other via the first oil component storage unit 22. Therefore, since the high-pressure air Air compressed in the compression chamber 30 does not flow into the working chamber 13 through the first oil content storage unit 22, the compressed air Air is discharged from the discharge port 16b without disappearing. That is, the disappearance of the compressed air Air can be suppressed.

なお、図４の（ａ）に図示される特異点Ｘ１，Ｘ２は、第１ロータ１１の歯部１１ｂに沿って螺旋状に連続して設けられて螺旋状の連続線を形成する。同様に、図４の（ａ）に図示される特異点Ｙ１，Ｙ２は、第２ロータ２０の歯溝２０ａに沿って螺旋状に連続して設けられて螺旋状の連続線を形成する。
そして第１開口部２２ａは、連続して設けられる特異点Ｘ１による連続線と、連続して設けられる特異点Ｘ２による連続線と、の間に形成される。 Note that the singular points X1 and X2 illustrated in FIG. 4A are continuously provided in a spiral shape along the tooth portion 11b of the first rotor 11 to form a spiral continuous line. Similarly, the singular points Y1 and Y2 illustrated in FIG. 4A are continuously provided spirally along the tooth groove 20a of the second rotor 20 to form a spiral continuous line.
And the 1st opening part 22a is formed between the continuous line by the singular point X1 provided continuously, and the continuous line by the singular point X2 provided continuously.

図６は、第１ロータの歯部にかき集められる作動油が油分収容部に流れ込む状態を示す図である。
図４の（ａ）に示すように第１油分収容部２２が形成される第１ロータ１１が回転すると、図６に示すように、第１ロータ１１の歯部１１ｂにかき集められる作動油Ｏｉｌは第１油分収容部２２に流れ込む。また、第２ロータ２０の歯部２０ｂにかき集められる作動油Ｏｉｌは、圧縮室３０で第１油分収容部２２に流れ込む。したがって、圧縮室３０に溜まる作動油Ｏｉｌの量は少なくなる。このため、圧縮室３０と連通している吐出口１６ｂが作動油Ｏｉｌで閉塞されることが抑制される。したがって、吐出口１６ｂからの空気Ａｉｒの吐出は妨げられず吐出抵抗は大きくならない。ひいては、吐出過程に圧縮室３０の圧力Ｐが低格の吐出圧力「Ｐｓｔｄ」よりも上昇する、図３に示すような圧力上昇が抑制される。 FIG. 6 is a diagram illustrating a state in which hydraulic oil collected on the teeth of the first rotor flows into the oil container.
As shown in FIG. 4 (a), when the first rotor 11 in which the first oil storage portion 22 is formed rotates, as shown in FIG. 6, the hydraulic oil Oil collected on the teeth 11b of the first rotor 11 is It flows into the first oil storage unit 22. In addition, the hydraulic oil Oil collected by the teeth 20 b of the second rotor 20 flows into the first oil component storage unit 22 in the compression chamber 30. Therefore, the amount of hydraulic oil Oil that accumulates in the compression chamber 30 is reduced. For this reason, it is suppressed that the discharge port 16b connected with the compression chamber 30 is obstruct | occluded with hydraulic oil Oil. Therefore, the discharge of air Air from the discharge port 16b is not hindered and the discharge resistance does not increase. As a result, the pressure increase as shown in FIG. 3 in which the pressure P of the compression chamber 30 rises above the low discharge pressure “Pstd” during the discharge process is suppressed.

また、吐出過程で第１油分収容部２２と連通するように吐出口１６ｂの形状が設定され、第１油分収容部２２に収容されている作動油Ｏｉｌが吐出口１６ｂから排出されるように構成される。このため、吐出完了時には第１油分収容部２２の作動油Ｏｉｌが全て排出される。特に、吐出完了時に、第１油分収容部２２の軸方向端面１１ｃの側が全領域に亘って吐出口１６ｂと連通する構成（つまり、吐出完了時に第１油分収容部２２の軸方向端面１１ｃの側が吐出口１６ｂと連通して全開する構成）とすれば、第１油分収容部２２に収容されている作動油Ｏｉｌが効果的に吐出口１６ｂから排出される。つまり、少なくとも吐出完了時に、第１油分収容部２２の軸方向端面１１ｃの側が全開するように、吐出口１６ｂが形成されていることが好ましい。
そして、圧縮過程で第１ロータ１１が回転するとき、新たな作動油Ｏｉｌが第１油分収容部２２に収容される。 Further, the shape of the discharge port 16b is set so as to communicate with the first oil component storage unit 22 in the discharge process, and the hydraulic oil Oil stored in the first oil component storage unit 22 is discharged from the discharge port 16b. Is done. For this reason, when the discharge is completed, all the hydraulic oil Oil in the first oil container 22 is discharged. In particular, when the discharge is completed, the configuration in which the axial end surface 11c side of the first oil component storage unit 22 communicates with the discharge port 16b over the entire region (that is, the axial end surface 11c side of the first oil component storage unit 22 when the discharge is completed is If it is configured to fully open by communicating with the discharge port 16b, the hydraulic oil Oil stored in the first oil content storage unit 22 is effectively discharged from the discharge port 16b. That is, it is preferable that the discharge port 16b is formed so that the side of the axial end surface 11c of the first oil component storage portion 22 is fully opened at least when the discharge is completed.
Then, when the first rotor 11 rotates in the compression process, new hydraulic oil Oil is stored in the first oil storage unit 22.

図７は、図６におけるＳｅｃ１−Ｓｅｃ１での断面図であり、油分収容部の形状を示す図である。
図７に示すように、実施例１の第１油分収容部２２は、第１開口部２２ａを臨む面（底面２２ｂ）が傾斜面になっている。具体的に、吐出口１６ｂと連通している第１油分収容部２２の底面２２ｂの法線Ｌ１を、回転軸１０ａ（図１参照）に平行な軸平行成分Ｌ１ｐと、回転軸１０ａと直交する軸垂直成分Ｌ１ｖと、に分解したとき、軸平行成分Ｌ１ｐが吐出口１６ｂの方向を向くように底面２２ｂが形成されている。 FIG. 7 is a cross-sectional view taken along Sec1-Sec1 in FIG. 6 and shows the shape of the oil content storage portion.
As shown in FIG. 7, in the first oil container 22 of the first embodiment, the surface (bottom surface 22 b) facing the first opening 22 a is an inclined surface. Specifically, the normal line L1 of the bottom surface 22b of the first oil component storage unit 22 communicating with the discharge port 16b is orthogonal to the axis parallel component L1p parallel to the rotation axis 10a (see FIG. 1) and the rotation axis 10a. The bottom surface 22b is formed so that the axial parallel component L1p faces the direction of the discharge port 16b when decomposed into the axial vertical component L1v.

底面２２ｂが図７に示すような傾斜面で形成されていると、第１ロータ１１の回転で第１油分収容部２２に収容された作動油Ｏｉｌには、底面２２ｂによって吐出口１６ｂの方向への速度成分が生じる。したがって、吐出過程で第１油分収容部２２が吐出口１６ｂと連通したとき、第１油分収容部２２に収容された作動油Ｏｉｌが効率よく吐出口１６ｂから排出される。   When the bottom surface 22b is formed as an inclined surface as shown in FIG. 7, the hydraulic oil stored in the first oil component storage unit 22 by the rotation of the first rotor 11 is directed toward the discharge port 16b by the bottom surface 22b. The speed component is generated. Accordingly, when the first oil component storage unit 22 communicates with the discharge port 16b during the discharge process, the hydraulic oil Oil stored in the first oil component storage unit 22 is efficiently discharged from the discharge port 16b.

以上のように、実施例１のスクリュー圧縮機１（図１参照）は、図４の（ａ），（ｂ）に示すように、第１ロータ１１の歯部１１ｂに、軸方向端面１１ｃが凹んで形成される第１油分収容部２２が設けられている。そして、圧縮過程で第１ロータ１１と第２ロータ２０の歯部１１ｂ，２０ｂでかき集められる作動油Ｏｉｌは、図６に示すように第１油分収容部２２に収容される。したがって、吐出過程で、作動油Ｏｉｌによる吐出口１６ｂの閉塞が抑制される。このため、吐出口１６ｂにおける空気Ａｉｒの吐出抵抗が小さくなり、空気Ａｉｒは圧縮室３０から吐出口１６ｂを介して効率よく吐出される。このことによって、吐出過程で圧縮室３０の圧力Ｐが吐出圧力「Ｐｓｔｄ」より昇圧することが抑制される。   As described above, the screw compressor 1 according to the first embodiment (see FIG. 1) has the axial end surface 11c on the tooth portion 11b of the first rotor 11 as shown in FIGS. 4 (a) and 4 (b). A first oil storage portion 22 formed in a recessed shape is provided. Then, the hydraulic oil Oil collected by the tooth portions 11b and 20b of the first rotor 11 and the second rotor 20 in the compression process is stored in the first oil content storage portion 22 as shown in FIG. Therefore, blockage of the discharge port 16b by the hydraulic oil Oil is suppressed during the discharge process. For this reason, the discharge resistance of the air Air in the discharge port 16b becomes small, and the air Air is efficiently discharged from the compression chamber 30 through the discharge port 16b. This suppresses the pressure P in the compression chamber 30 from being raised from the discharge pressure “Pstd” during the discharge process.

また、図６に示すように、第１ロータ１１の回転でかき集められる作動油Ｏｉｌが第１油分収容部２２に収容されるため、吐出過程で圧縮室３０に溜まる作動油Ｏｉｌが減少する。このことによっても、吐出過程における作動油Ｏｉｌによる吐出口１６ｂの閉塞が抑制される。   Further, as shown in FIG. 6, since the hydraulic oil Oil collected by the rotation of the first rotor 11 is stored in the first oil content storage unit 22, the hydraulic oil Oil that accumulates in the compression chamber 30 during the discharge process decreases. This also prevents the discharge port 16b from being blocked by the hydraulic oil Oil during the discharge process.

また、圧縮室３０で圧縮された高圧の空気Ａｉｒが第１油分収容部２２を流通して作動室１３に流れ込まない。したがって、圧縮された空気Ａｉｒの消失が抑制され、圧縮された空気Ａｉｒの消失にともなうロスが軽減される。   Further, the high-pressure air Air compressed in the compression chamber 30 does not flow into the working chamber 13 through the first oil content storage unit 22. Therefore, the loss | disappearance of the compressed air Air is suppressed and the loss accompanying the loss | disappearance of the compressed air Air is reduced.

図８の（ａ）は、実施例２の油分収容部を示す図、（ｂ）は、油分収容部の斜視図である。
なお、実施例２の第１ロータと第２ロータが備わるスクリュー圧縮機は、図１，図２に示す実施例１のスクリュー圧縮機１と同じ構成である。したがって、実施例１のスクリュー圧縮機１と同じ構成要素には、図１，図２と同じ符号を付して詳細な説明は省略する。 (A) of FIG. 8 is a figure which shows the oil content accommodating part of Example 2, (b) is a perspective view of an oil content accommodating part.
The screw compressor provided with the first rotor and the second rotor of the second embodiment has the same configuration as the screw compressor 1 of the first embodiment shown in FIGS. Therefore, the same components as those of the screw compressor 1 of the first embodiment are denoted by the same reference numerals as those in FIGS. 1 and 2 and detailed description thereof is omitted.

図８の（ａ）、（ｂ）に示すように、実施例２では、第１ロータ１１に形成される第１油分収容部２２（図４の（ａ）参照）に替わって第２ロータ２０の歯部２０ｂに第２凹部（第２油分収容部２３）が設けられている。
実施例２の第２ロータ２０に形成される第２油分収容部２３は、歯部２０ｂの軸方向端面２０ｃが、回転軸１０ｂ（図２参照）の軸方向に向かって凹んで形成される。 As shown in FIGS. 8A and 8B, in the second embodiment, the second rotor 20 is replaced with the first oil container 22 (see FIG. 4A) formed in the first rotor 11. The tooth part 20b is provided with a second recess (second oil storage part 23).
The second oil storage portion 23 formed in the second rotor 20 of the second embodiment is formed such that the axial end surface 20c of the tooth portion 20b is recessed toward the axial direction of the rotating shaft 10b (see FIG. 2).

また、第２油分収容部２３には、歯部２０ｂの歯先２０ｂ１に第２開口部２３ａが形成される。そして、作動室１３と第２油分収容部２３が第２開口部２３ａを介して連通する。さらに、第２開口部２３ａが、第２ロータ２０の歯部２０ｂのピッチ円Ｃ１よりも外側（歯先２０ｂ１の側）に開口している。   Moreover, the 2nd opening part 23a is formed in the tooth tip 20b1 of the tooth | gear part 20b in the 2nd oil content accommodating part 23. FIG. And the working chamber 13 and the 2nd oil content accommodating part 23 are connected via the 2nd opening part 23a. Furthermore, the 2nd opening part 23a is opening outside the pitch circle C1 of the tooth part 20b of the 2nd rotor 20 (the side of the tooth tip 20b1).

空気Ａｉｒを圧縮する圧縮室３０は、第２ロータ２０の歯溝２０ａに第１ロータ１１の歯部１１ｂが噛み合って形成される。したがって、第２ロータ２０の歯部２０ｂのピッチ円Ｃ１より外側（歯先２０ｂ１の側）に開口する第２開口部２３ａは圧縮室３０に入り込まない。このため、第２開口部２３ａは圧縮室３０で開口せず、圧縮室３０と作動室１３が第２油分収容部２３を介して連通しない。   The compression chamber 30 for compressing the air Air is formed by engaging the tooth portion 11 b of the first rotor 11 with the tooth groove 20 a of the second rotor 20. Therefore, the second opening 23 a that opens outside the pitch circle C <b> 1 of the tooth portion 20 b of the second rotor 20 (the tooth tip 20 b 1 side) does not enter the compression chamber 30. For this reason, the second opening 23 a does not open in the compression chamber 30, and the compression chamber 30 and the working chamber 13 do not communicate with each other via the second oil storage portion 23.

また、圧縮過程で第１ロータ１１の歯部１１ｂと第２ロータ２０の歯部２０ｂにかき集められた作動油Ｏｉｌは、作動室１３で開口する第２開口部２３ａから第２油分収容部２３に収容される。したがって、圧縮室３０において吐出口１６ｂが開口する部分に溜まる作動油Ｏｉｌの量が少なくなり、吐出口１６ｂにおける空気Ａｉｒの吐出抵抗が小さくなる。   In addition, the hydraulic oil Oil collected in the tooth portion 11b of the first rotor 11 and the tooth portion 20b of the second rotor 20 in the compression process is transferred from the second opening portion 23a opened in the working chamber 13 to the second oil content housing portion 23. Be contained. Accordingly, the amount of hydraulic oil Oil that accumulates in the portion where the discharge port 16b opens in the compression chamber 30 is reduced, and the discharge resistance of the air Air at the discharge port 16b is reduced.

また、吐出過程で第２油分収容部２３と連通するように吐出口１６ｂの形状が設定され、第２油分収容部２３に収容されている作動油Ｏｉｌが吐出口１６ｂから排出されるように構成される。このため、吐出完了時には第２油分収容部２３の作動油Ｏｉｌが全て排出される。特に、吐出完了時に、第２油分収容部２３の軸方向端面２０ｃの側が全領域に亘って吐出口１６ｂと連通する構成（つまり、吐出完了時に第２油分収容部２３の軸方向端面２０ｃの側が吐出口１６ｂと連通して全開する構成）とすれば、第２油分収容部２３に収容されている作動油Ｏｉｌが効果的に吐出口１６ｂから排出される。そして、圧縮過程で第２ロータ２０が回転するとき、新たな作動油Ｏｉｌが第２油分収容部２３に収容される。つまり、少なくとも吐出完了時に、第２油分収容部２３の軸方向端面２０ｃの側が全開するように、吐出口１６ｂが形成されていることが好ましい。   Further, the shape of the discharge port 16b is set so as to communicate with the second oil component storage unit 23 in the discharge process, and the hydraulic oil Oil stored in the second oil component storage unit 23 is discharged from the discharge port 16b. Is done. For this reason, when the discharge is completed, all the hydraulic oil Oil in the second oil content storage unit 23 is discharged. Particularly, when the discharge is completed, the configuration in which the side of the axial end surface 20c of the second oil component storage portion 23 communicates with the discharge port 16b over the entire region (that is, the side of the axial end surface 20c of the second oil content storage portion 23 when the discharge is completed is If it is configured to communicate with the discharge port 16b and fully open, the hydraulic oil Oil stored in the second oil content storage portion 23 is effectively discharged from the discharge port 16b. And when the 2nd rotor 20 rotates in a compression process, new hydraulic oil Oil is accommodated in the 2nd oil content accommodating part 23. FIG. That is, it is preferable that the discharge port 16b is formed so that the side of the axial end surface 20c of the second oil component storage portion 23 is fully opened at least when the discharge is completed.

また、実施例２の第２油分収容部２３も、第２開口部２３ａを臨む底面２３ｂが傾斜面になっていることが好ましい。つまり、図示はしないが、底面２３ｂの法線を、軸平行成分と、軸垂直成分と、に分解したとき、軸平行成分が吐出口１６ｂ（図２参照）の方向を向くように底面２３ｂが形成されていることが好ましい。   Moreover, it is preferable that the bottom face 23b which faces the 2nd opening part 23a also in the 2nd oil content accommodating part 23 of Example 2 is an inclined surface. That is, although not shown, when the normal line of the bottom surface 23b is decomposed into an axial parallel component and an axial vertical component, the bottom surface 23b is oriented so that the axial parallel component faces the direction of the discharge port 16b (see FIG. 2). Preferably it is formed.

以上のように、実施例２のスクリュー圧縮機は、図８の（ａ），（ｂ）に示すように、第２ロータ２０の歯部２０ｂに、軸方向端面２０ｃが凹んだ第２油分収容部２３が設けられている。そして、圧縮過程で第１ロータ１１と第２ロータ２０の歯部１１ｂ，２０ｂでかき集められた作動油Ｏｉｌは第２油分収容部２３に収容される。したがって、吐出過程で、作動油Ｏｉｌによる吐出口１６ｂの閉塞が抑制される。このため、吐出口１６ｂにおける空気Ａｉｒの吐出抵抗が小さくなり、空気Ａｉｒは吐出口１６ｂから効率よく吐出される。このことによって、吐出過程において圧縮室３０の圧力Ｐが吐出圧力「Ｐｓｔｄ」より昇圧する圧力上昇が抑制される。   As described above, the screw compressor of the second embodiment accommodates the second oil component in which the axial end face 20c is recessed in the tooth portion 20b of the second rotor 20, as shown in FIGS. A portion 23 is provided. The hydraulic oil Oil collected by the tooth portions 11 b and 20 b of the first rotor 11 and the second rotor 20 in the compression process is stored in the second oil content storage portion 23. Therefore, blockage of the discharge port 16b by the hydraulic oil Oil is suppressed during the discharge process. For this reason, the discharge resistance of the air Air in the discharge port 16b becomes small, and the air Air is efficiently discharged from the discharge port 16b. As a result, the pressure increase in which the pressure P of the compression chamber 30 is increased from the discharge pressure “Pstd” in the discharge process is suppressed.

また、実施例１と同様に、第１ロータ１１と第２ロータ２０の回転でかき集められる作動油Ｏｉｌが第２油分収容部２３に収容されるため、吐出過程で圧縮室３０に溜まる作動油Ｏｉｌが減少する。このことによっても、吐出過程における作動油Ｏｉｌによる吐出口１６ｂの閉塞が抑制される。   Similarly to the first embodiment, since the hydraulic oil Oil collected by the rotation of the first rotor 11 and the second rotor 20 is stored in the second oil content storage portion 23, the hydraulic oil Oil that accumulates in the compression chamber 30 during the discharge process. Decrease. This also prevents the discharge port 16b from being blocked by the hydraulic oil Oil during the discharge process.

また、第２油分収容部２３の第２開口部２３ａは、第２ロータ２０のピッチ円Ｃ１よりも外側（歯先２０ｂ１の側）に開口している。この構成によって、第２開口部２３ａは圧縮室３０で開口しない。このため、圧縮室３０と作動室１３は第２油分収容部２３を介して連通しない。したがって、圧縮室３０で圧縮された高圧の空気Ａｉｒが第２油分収容部２３を流通して作動室１３に流れ込むことがない。よって、圧縮された空気Ａｉｒの消失が抑制されるため、圧縮された空気Ａｉｒの消失にともなうロスが軽減される。   In addition, the second opening 23 a of the second oil component storage unit 23 is open to the outer side (the tooth tip 20 b 1 side) than the pitch circle C 1 of the second rotor 20. With this configuration, the second opening 23 a is not opened in the compression chamber 30. For this reason, the compression chamber 30 and the working chamber 13 do not communicate with each other via the second oil content storage portion 23. Therefore, the high-pressure air Air compressed in the compression chamber 30 does not flow through the second oil content storage portion 23 and flow into the working chamber 13. Therefore, since the loss | disappearance of the compressed air Air is suppressed, the loss accompanying the loss | disappearance of the compressed air Air is reduced.

なお、本発明は前記した実施例に限定されるものではない。例えば、前記した実施例は本発明をわかりやすく説明するために詳細に説明したものであり、必ずしも説明した全ての構成を備えるものに限定されるものではない。
また、ある実施例の構成の一部を他の実施例の構成に置き換えることも可能であり、また、ある実施例の構成に他の実施例の構成を加えることも可能である。 In addition, this invention is not limited to an above-described Example. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.
Further, a part of the configuration of a certain embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of a certain embodiment.

例えば、実施例１のスクリュー圧縮機は、図４の（ａ）に示すように、第１ロータ１１の歯部１１ｂに第１油分収容部２２が設けられる。また、実施例２のスクリュー圧縮機は、図８の（ａ）に示すように、第２ロータ２０の歯部２０ｂに第２油分収容部２３が設けられる。そこで、実施例１と実施例２を組み合わせ、第１ロータ１１の歯部１１ｂに第１油分収容部２２が設けられ、かつ、第２ロータ２０の歯部２０ｂに第２油分収容部２３が設けられるスクリュー圧縮機であってもよい。
なお、この場合には、少なくとも吐出完了時に、第１油分収容部２２の軸方向端面１１ｃの側が全開し、かつ、第２油分収容部２３の軸方向端面２０ｃの側が全開するように、吐出口１６ｂが形成されていることが好ましい。 For example, as shown in FIG. 4A, the screw compressor of the first embodiment is provided with the first oil content storage portion 22 in the tooth portion 11 b of the first rotor 11. Further, in the screw compressor of the second embodiment, as shown in FIG. 8A, the second oil content storage portion 23 is provided on the tooth portion 20 b of the second rotor 20. Therefore, the first and second embodiments are combined, and the first oil component accommodating portion 22 is provided in the tooth portion 11b of the first rotor 11, and the second oil component accommodating portion 23 is provided in the tooth portion 20b of the second rotor 20. It may be a screw compressor.
In this case, at least when discharge is completed, the discharge port is such that the side of the axial end surface 11c of the first oil component storage unit 22 is fully opened and the side of the axial end surface 20c of the second oil component storage unit 23 is fully open. 16b is preferably formed.

この他、本発明は、前記した実施例に限定されるものではなく、発明の趣旨を逸脱しない範囲で適宜変更が可能である。
例えば、図４の（ａ）に示す第１油分収容部２２の形状や、図８の（ａ）に示す第２油分収容部２３の形状は一例に過ぎず、それらの形状は限定されない。
つまり、図４の（ａ）に示す第１開口部２２ａが前記した特異点Ｘ１，Ｘ２の間に開口する構成であれば、第１油分収容部２２の形状は限定されない。また、図８の（ａ）に示す第２開口部２３ａがピッチ円Ｃ１よりも外側に開口する構成であれば、第２油分収容部２３の形状は限定されない。但し、第１開口部２２ａ，第２開口部２３ａの形状は、作動油Ｏｉｌが第１油分収容部２２，第２油分収容部２３に容易に流入する形状であることが好ましい。 In addition, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the invention.
For example, the shape of the first oil component storage unit 22 shown in FIG. 4A and the shape of the second oil component storage unit 23 shown in FIG. 8A are merely examples, and these shapes are not limited.
That is, as long as the first opening 22a shown in FIG. 4A is configured to open between the singular points X1 and X2, the shape of the first oil component storage unit 22 is not limited. Moreover, if the 2nd opening part 23a shown to (a) of FIG. 8 is the structure opened outside pitch circle C1, the shape of the 2nd oil content accommodating part 23 will not be limited. However, it is preferable that the shape of the first opening 22a and the second opening 23a is a shape in which the hydraulic oil Oil easily flows into the first oil component storage unit 22 and the second oil component storage unit 23.

１ スクリュー圧縮機
１０ａ 回転軸（第１ロータの回転軸）
１０ｂ 回転軸（第２ロータの回転軸）
１１ 第１ロータ
１１ａ，２０ａ 歯溝
１１ｂ，２０ｂ 歯部
１１ｂ１，２０ｂ１ 歯先
１１ｃ，２０ｃ 軸方向端面
１２ ケーシング
１３ 作動室
１６ｂ 吐出口
２０ 第２ロータ
２０ａ１ 歯底
２２ 第１油分収容部（第１凹部）
２２ａ 第１開口部
２２ｂ，２３ｂ 底面
２３ 第２油分収容部（第２凹部）
２３ａ 第２開口部
３０ 圧縮室
Ａｉｒ 空気（作動流体） 1 Screw compressor 10a Rotating shaft (Rotating shaft of the first rotor)
10b Rotating shaft (Rotating shaft of the second rotor)
11 First rotor 11a, 20a Tooth groove 11b, 20b Tooth part 11b1, 20b1 Tooth tip 11c, 20c Axial end face 12 Casing 13 Working chamber 16b Discharge port 20 Second rotor 20a1 Tooth bottom 22 First oil content storage part (first recess) )
22a 1st opening part 22b, 23b Bottom face 23 2nd oil content accommodating part (2nd recessed part)
23a 2nd opening part 30 Compression chamber Air Air (working fluid)

Claims (9)

ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、
前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、
前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、
前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、
前記第１ロータの歯部に、軸方向端面が凹んだ第１凹部が形成され、
前記第１凹部は前記第１ロータの歯部の歯先に形成される第１開口部で前記作動室または前記圧縮室と連通し、
前記第１開口部は、前記圧縮室が消滅したときに前記第１ロータの歯部の歯先と前記第２ロータの歯溝の歯底が重なりあう位置に開口し、
前記第１凹部において前記第１開口部を臨む底面の法線は、前記第１ロータの回転軸の軸線方向の成分が、軸方向端面に向かい合う前記作動室内の端面の方向を向く
ことを特徴とするスクリュー圧縮機。 A first rotor and a second rotor that mesh with each other in a working chamber in the casing and rotate to compress the working fluid;
A discharge port that opens to an end surface in the working chamber facing the axial end surfaces of the first rotor and the second rotor,
The working fluid is provided to communicate with the compression chamber after being compressed as the compression chamber formed in the tooth groove of the second rotor meshed with the teeth of the first rotor. Discharged to the outside of the casing through the discharge port,
The compression chamber shrinks until it disappears and discharges the working fluid,
A first concave portion having a concave axial end surface is formed in the tooth portion of the first rotor,
The first recess communicates with the working chamber or the compression chamber at a first opening formed at a tooth tip of a tooth portion of the first rotor,
The first opening opens at a position where the tooth tip of the tooth portion of the first rotor and the tooth bottom of the tooth space of the second rotor overlap when the compression chamber disappears ,
The normal line of the bottom surface facing the first opening in the first recess is such that the axial component of the rotation axis of the first rotor faces the end surface in the working chamber facing the axial end surface. A screw compressor characterized by that. 少なくとも前記圧縮室が消滅した時点で、前記第２ロータの歯溝に噛み合っている前記第１ロータの歯部に形成されている前記第１凹部の軸方向端面の側が前記吐出口と連通して全開することを特徴とする請求項１に記載のスクリュー圧縮機。 At least when the compression chamber disappears, the axial end face side of the first recess formed in the tooth portion of the first rotor meshing with the tooth groove of the second rotor communicates with the discharge port. The screw compressor according to claim 1 , wherein the screw compressor is fully opened. ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、  A first rotor and a second rotor that mesh with each other in a working chamber in the casing and rotate to compress the working fluid;
前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、  A discharge port that opens to an end surface in the working chamber facing the axial end surfaces of the first rotor and the second rotor,
前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、  The working fluid is provided to communicate with the compression chamber after being compressed as the compression chamber formed in the tooth groove of the second rotor meshed with the teeth of the first rotor. Discharged to the outside of the casing through the discharge port,
前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、  The compression chamber shrinks until it disappears and discharges the working fluid,
前記第１ロータの歯部に、軸方向端面が凹んだ第１凹部が形成され、  A first concave portion having a concave axial end surface is formed in the tooth portion of the first rotor,
前記第１凹部は前記第１ロータの歯部の歯先に形成される第１開口部で前記作動室または前記圧縮室と連通し、  The first recess communicates with the working chamber or the compression chamber at a first opening formed at a tooth tip of a tooth portion of the first rotor,
前記第１開口部は、前記圧縮室が消滅したときに前記第１ロータの歯部の歯先と前記第２ロータの歯溝の歯底が重なりあう位置に開口し、  The first opening opens at a position where the tooth tip of the tooth portion of the first rotor and the tooth bottom of the tooth space of the second rotor overlap when the compression chamber disappears,
少なくとも前記圧縮室が消滅した時点で、前記第２ロータの歯溝に噛み合っている前記第１ロータの歯部に形成されている前記第１凹部の軸方向端面の側が前記吐出口と連通して全開する  At least when the compression chamber disappears, the axial end face side of the first recess formed in the tooth portion of the first rotor meshing with the tooth groove of the second rotor communicates with the discharge port. Fully open
ことを特徴とするスクリュー圧縮機。A screw compressor characterized by that. ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、
前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、
前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、
前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、
前記第２ロータの歯部に、軸方向端面が凹んだ第２凹部が形成され、
前記第２凹部は前記第２ロータの歯部の歯先に形成される第２開口部で前記作動室と連通し、
前記第２開口部は、前記第２ロータのピッチ円よりも外側に開口し、
前記第２凹部において前記第２開口部を臨む底面の法線は、前記第２ロータの回転軸の軸線方向の成分が、軸方向端面に向かい合う前記作動室内の端面の方向を向く
ことを特徴とするスクリュー圧縮機。 A first rotor and a second rotor that mesh with each other in a working chamber in the casing and rotate to compress the working fluid;
A discharge port that opens to an end surface in the working chamber facing the axial end surfaces of the first rotor and the second rotor,
The working fluid is provided to communicate with the compression chamber after being compressed as the compression chamber formed in the tooth groove of the second rotor meshed with the teeth of the first rotor. Discharged to the outside of the casing through the discharge port,
The compression chamber shrinks until it disappears and discharges the working fluid,
A second concave portion having a concave axial end surface is formed in the tooth portion of the second rotor,
The second recess communicates with the working chamber at a second opening formed at a tooth tip of a tooth portion of the second rotor,
The second opening opens outside the pitch circle of the second rotor ,
The normal line of the bottom surface facing the second opening in the second recess has the axial component of the rotation axis of the second rotor directed toward the end surface in the working chamber facing the axial end surface. A screw compressor characterized by that. 少なくとも前記圧縮室が消滅した時点で、前記第１ロータの歯溝に噛み合っている前記第２ロータの歯部に形成されている前記第２凹部の軸方向端面の側が前記吐出口と連通して全開することを特徴とする請求項４に記載のスクリュー圧縮機。 At least when the compression chamber disappears, the axial end face side of the second recess formed in the tooth portion of the second rotor meshing with the tooth groove of the first rotor communicates with the discharge port. The screw compressor according to claim 4 , wherein the screw compressor is fully opened. ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、  A first rotor and a second rotor that mesh with each other in a working chamber in the casing and rotate to compress the working fluid;
前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、  A discharge port that opens to an end surface in the working chamber facing the axial end surfaces of the first rotor and the second rotor,
前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、  The working fluid is provided to communicate with the compression chamber after being compressed as the compression chamber formed in the tooth groove of the second rotor meshed with the teeth of the first rotor. Discharged to the outside of the casing through the discharge port,
前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、  The compression chamber shrinks until it disappears and discharges the working fluid,
前記第２ロータの歯部に、軸方向端面が凹んだ第２凹部が形成され、  A second concave portion having a concave axial end surface is formed in the tooth portion of the second rotor,
前記第２凹部は前記第２ロータの歯部の歯先に形成される第２開口部で前記作動室と連通し、  The second recess communicates with the working chamber at a second opening formed at a tooth tip of a tooth portion of the second rotor,
前記第２開口部は、前記第２ロータのピッチ円よりも外側に開口し、  The second opening opens outside the pitch circle of the second rotor,
少なくとも前記圧縮室が消滅した時点で、前記第１ロータの歯溝に噛み合っている前記第２ロータの歯部に形成されている前記第２凹部の軸方向端面の側が前記吐出口と連通して全開することを特徴とするスクリュー圧縮機。  At least when the compression chamber disappears, the axial end face side of the second recess formed in the tooth portion of the second rotor meshing with the tooth groove of the first rotor communicates with the discharge port. Screw compressor characterized by fully opening. ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、
前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、
前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、
前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、
前記第１ロータの歯部に、軸方向端面が凹んだ第１凹部が形成されて、前記第２ロータの歯部に、軸方向端面が凹んだ第２凹部が形成され、
前記第１凹部は前記第１ロータの歯部の歯先に形成される第１開口部で前記作動室または前記圧縮室と連通し、
前記第１開口部は、前記圧縮室が消滅したときに前記第１ロータの歯部の歯先と前記第２ロータの歯溝の歯底が重なりあう位置に開口し、
前記第２凹部は前記第２ロータの歯部の歯先に形成される第２開口部で前記作動室と連通し、
前記第２開口部は、前記第２ロータのピッチ円よりも外側に開口し、
前記第１凹部において前記第１開口部を臨む底面の法線は、前記第１ロータの回転軸の軸線方向の成分が、軸方向端面に向かい合う前記作動室内の端面の方向を向き、
前記第２凹部において前記第２開口部を臨む底面の法線は、前記第２ロータの回転軸の軸線方向の成分が、軸方向端面に向かい合う前記作動室内の端面の方向を向く
ことを特徴とするスクリュー圧縮機。 A first rotor and a second rotor that mesh with each other in a working chamber in the casing and rotate to compress the working fluid;
A discharge port that opens to an end surface in the working chamber facing the axial end surfaces of the first rotor and the second rotor,
The working fluid is provided to communicate with the compression chamber after being compressed as the compression chamber formed in the tooth groove of the second rotor meshed with the teeth of the first rotor. Discharged to the outside of the casing through the discharge port,
The compression chamber shrinks until it disappears and discharges the working fluid,
A first concave portion having a concave axial end surface is formed in the tooth portion of the first rotor, and a second concave portion having a concave axial end surface is formed in the tooth portion of the second rotor,
The first recess communicates with the working chamber or the compression chamber at a first opening formed at a tooth tip of a tooth portion of the first rotor,
The first opening opens at a position where the tooth tip of the tooth portion of the first rotor and the tooth bottom of the tooth space of the second rotor overlap when the compression chamber disappears,
The second recess communicates with the working chamber at a second opening formed at a tooth tip of a tooth portion of the second rotor,
The second opening opens outside the pitch circle of the second rotor ,
The normal line of the bottom surface facing the first opening in the first recess has the axial component of the rotation axis of the first rotor oriented in the direction of the end surface in the working chamber facing the axial end surface,
The normal line of the bottom surface facing the second opening in the second recess has the axial component of the rotation axis of the second rotor directed toward the end surface in the working chamber facing the axial end surface. A screw compressor characterized by that. 少なくとも前記圧縮室が消滅した時点で、
前記第２ロータの歯溝に噛み合っている前記第１ロータの歯部に形成されている前記第１凹部の軸方向端面の側が前記吐出口と連通して全開し、
前記第１ロータの歯溝に噛み合っている前記第２ロータの歯部に形成されている前記第２凹部の軸方向端面の側が前記吐出口と連通して全開することを特徴とする請求項７に記載のスクリュー圧縮機。 At least when the compression chamber disappears,
The side of the axial end surface of the first recess formed in the tooth portion of the first rotor meshing with the tooth groove of the second rotor communicates with the discharge port and is fully opened,
Claim 7, characterized in that the side of the axial end surface of said second recess formed in the teeth of the second rotor meshing with tooth spaces of the first rotor is fully opened in communication with the discharge port The screw compressor described in 1. ケーシング内の作動室で互いに噛み合って回転して作動流体を圧縮する第１ロータおよび第２ロータと、  A first rotor and a second rotor that mesh with each other in a working chamber in the casing and rotate to compress the working fluid;
前記第１ロータおよび前記第２ロータの軸方向端面に向かい合う前記作動室内の端面に開口する吐出口と、を有し、  A discharge port that opens to an end surface in the working chamber facing the axial end surfaces of the first rotor and the second rotor,
前記作動流体は、前記第１ロータの歯部が噛み合った前記第２ロータの歯溝に形成される圧縮室の縮小にともなって圧縮された後に、前記圧縮室と連通するように設けられている前記吐出口を通って前記ケーシングの外部に吐出され、  The working fluid is provided to communicate with the compression chamber after being compressed as the compression chamber formed in the tooth groove of the second rotor meshed with the teeth of the first rotor. Discharged to the outside of the casing through the discharge port,
前記圧縮室は消滅するまで縮小して前記作動流体を吐出し、  The compression chamber shrinks until it disappears and discharges the working fluid,
前記第１ロータの歯部に、軸方向端面が凹んだ第１凹部が形成されて、前記第２ロータの歯部に、軸方向端面が凹んだ第２凹部が形成され、  A first concave portion having a concave axial end surface is formed in the tooth portion of the first rotor, and a second concave portion having a concave axial end surface is formed in the tooth portion of the second rotor,
前記第１凹部は前記第１ロータの歯部の歯先に形成される第１開口部で前記作動室または前記圧縮室と連通し、  The first recess communicates with the working chamber or the compression chamber at a first opening formed at a tooth tip of a tooth portion of the first rotor,
前記第１開口部は、前記圧縮室が消滅したときに前記第１ロータの歯部の歯先と前記第２ロータの歯溝の歯底が重なりあう位置に開口し、  The first opening opens at a position where the tooth tip of the tooth portion of the first rotor and the tooth bottom of the tooth space of the second rotor overlap when the compression chamber disappears,
前記第２凹部は前記第２ロータの歯部の歯先に形成される第２開口部で前記作動室と連通し、  The second recess communicates with the working chamber at a second opening formed at a tooth tip of a tooth portion of the second rotor,
前記第２開口部は、前記第２ロータのピッチ円よりも外側に開口し、  The second opening opens outside the pitch circle of the second rotor,
少なくとも前記圧縮室が消滅した時点で、  At least when the compression chamber disappears,
前記第２ロータの歯溝に噛み合っている前記第１ロータの歯部に形成されている前記第１凹部の軸方向端面の側が前記吐出口と連通して全開し、  The side of the axial end surface of the first recess formed in the tooth portion of the first rotor meshing with the tooth groove of the second rotor communicates with the discharge port and is fully opened,
前記第１ロータの歯溝に噛み合っている前記第２ロータの歯部に形成されている前記第２凹部の軸方向端面の側が前記吐出口と連通して全開することを特徴とするスクリュー圧縮機。  A screw compressor characterized in that an axial end face side of the second recess formed in a tooth portion of the second rotor meshing with a tooth groove of the first rotor communicates with the discharge port and is fully opened. .
JP2013225764A 2013-10-30 2013-10-30 Screw compressor Active JP6184837B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2013225764A JP6184837B2 (en) 2013-10-30 2013-10-30 Screw compressor
CN201410412367.4A CN104595185B (en) 2013-10-30 2014-08-20 Screw compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2013225764A JP6184837B2 (en) 2013-10-30 2013-10-30 Screw compressor

Publications (2)

Publication Number Publication Date
JP2015086782A JP2015086782A (en) 2015-05-07
JP6184837B2 true JP6184837B2 (en) 2017-08-23

Family

ID=53049831

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2013225764A Active JP6184837B2 (en) 2013-10-30 2013-10-30 Screw compressor

Country Status (2)

Country Link
JP (1) JP6184837B2 (en)
CN (1) CN104595185B (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7037448B2 (en) * 2018-07-20 2022-03-16 株式会社日立産機システム Screw compressor body
JP7271392B2 (en) * 2019-10-30 2023-05-11 株式会社日立産機システム Feed screw compressor

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2811570A1 (en) * 1978-03-16 1979-09-20 Aerzener Maschf Gmbh SCREW COMPRESSOR
FR2609310B1 (en) * 1987-01-06 1991-04-12 Baudot Hardoll Sa SCREW TYPE ROTOR PROFILES FOR ROTATING MACHINES CARRYING A GASEOUS FLUID
JPS6445989A (en) * 1987-08-11 1989-02-20 Hitachi Ltd Screw fluid machine
RU2086808C1 (en) * 1995-01-10 1997-08-10 Владимир Ильич Масютин Screw machine rotors
JPH10159766A (en) * 1996-11-26 1998-06-16 Hitachi Ltd Oilless screw fluid machine
JP2002013494A (en) * 2000-06-29 2002-01-18 Tochigi Fuji Ind Co Ltd Fluid machine
JP5000962B2 (en) * 2006-09-28 2012-08-15 株式会社日立産機システム Screw compressor
JP5422260B2 (en) * 2009-05-28 2014-02-19 株式会社日立製作所 Oil-free screw compressor

Also Published As

Publication number Publication date
JP2015086782A (en) 2015-05-07
CN104595185B (en) 2017-04-12
CN104595185A (en) 2015-05-06

Similar Documents

Publication Publication Date Title
JP5765379B2 (en) Scroll compressor
JP5591049B2 (en) Internal gear type fluidic device
JP5691352B2 (en) Scroll compressor
JP6377839B2 (en) Gas compressor
EP2597311B1 (en) Single Screw Compressor With High Output
JP5422260B2 (en) Oil-free screw compressor
JP5000962B2 (en) Screw compressor
CN105190037B (en) Gear with engaging tooth
JP6184837B2 (en) Screw compressor
CN108884832B (en) Oil-cooled screw compressor
JP5178612B2 (en) Screw compressor
JP2008297944A (en) Screw compressor
JP6705200B2 (en) Screw compressor
JP6906887B2 (en) Scroll fluid machine
JP4821660B2 (en) Single screw compressor
JP7049473B2 (en) Screw compressor
CN209761718U (en) Screw compressor
CN210127943U9 (en) Screw compressor
US20160208801A1 (en) High Pressure, Single Stage Rotor
JP6599099B2 (en) Scroll fluid machinery
JP5775016B2 (en) Screw compressor
JP6444786B2 (en) Scroll compressor
JP2019173590A (en) Screw compressor
WO2022085631A1 (en) Screw compressor and screw rotor
JP6873763B2 (en) Screw fluid machine

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20160621

RD02 Notification of acceptance of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7422

Effective date: 20160708

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20160803

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20170317

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20170328

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20170529

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20170711

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20170726

R150 Certificate of patent or registration of utility model

Ref document number: 6184837

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150