JP5631236B2

JP5631236B2 - Pump and heat pump device

Info

Publication number: JP5631236B2
Application number: JP2011034185A
Authority: JP
Inventors: 訓明松永; 洋樹麻生
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2011-02-21
Filing date: 2011-02-21
Publication date: 2014-11-26
Anticipated expiration: 2031-02-21
Also published as: GB2488219A; JP2012172565A; GB2488219B; GB201202414D0

Description

この発明は、液体を搬送するポンプおよびポンプを備えたヒートポンプ装置に関するものである。 The present invention relates to a pump for transporting a liquid and a heat pump device including the pump.

図１５は、ヒートポンプ装置に使用される従来（特許文献１の図２）のポンプの断面図である。このポンプは、ステータ部１７と、ロータ部２１と、ポンプ部２６と、軸２７とを備える。軸２７の下端部は下ケーシング１５に、上端部は上ケーシング２４の軸支持部にそれぞれ自在に回転しないように拘束固定されていて、その周囲をロータ部２１が自在に回転する。ロータ部２１は、外周側に磁石部２０、内周側に軸受１８を具備し、磁石部２０と軸受１８は熱可塑性樹脂などの結合部材１９により一体に成形されている。この結合部材１９は羽根プレート下２５ｂも同時に形成している。さらに羽根プレート上２５ａと羽根プレート下２５ｂの間に、中心から放射状に複数の円弧状やインボリュート曲線状に形成した羽根２５ｃを挟み込むことにより羽根車２５を形成させている。羽根車２５が回転することにより、液体に遠心力を作用させて液体が吸入口２２から吐出口２３へ圧送される。 FIG. 15 is a cross-sectional view of a conventional pump (FIG. 2 of Patent Document 1) used in a heat pump device. This pump includes a stator portion 17, a rotor portion 21, a pump portion 26, and a shaft 27. The lower end portion of the shaft 27 is fixed to the lower casing 15 and the upper end portion is constrained and fixed so as not to freely rotate to the shaft supporting portion of the upper casing 24, and the rotor portion 21 freely rotates around the periphery. The rotor portion 21 includes a magnet portion 20 on the outer peripheral side and a bearing 18 on the inner peripheral side, and the magnet portion 20 and the bearing 18 are integrally formed by a coupling member 19 such as a thermoplastic resin. The coupling member 19 also forms a lower blade plate 25b at the same time. Further, the impeller 25 is formed by sandwiching blades 25c formed in a plurality of arcs or involute curves radially from the center between the blade plate upper 25a and the blade plate lower 25b. As the impeller 25 rotates, a centrifugal force is applied to the liquid, and the liquid is pumped from the suction port 22 to the discharge port 23.

軸支持部３５は逆円錐状の複数の脚形状を成し、軸２７の位置及びスラスト力を受けるスラストワッシャー２８の位置を保持する機能を有し、羽根プレート上２５ａの吸込穴３６の中に嵌め入れている。 The shaft support portion 35 has a plurality of inverted conical leg shapes, and has a function of holding the position of the shaft 27 and the position of the thrust washer 28 that receives the thrust force. The shaft support portion 35 is located in the suction hole 36 on the blade plate 25a. It is inserted.

ステータ部１７は電磁鋼板を積層して形成される鉄心１０と、この鉄心１０のスロット（図示せず）にインシュレータ１２（絶縁部材）を介して巻回される巻線１１と、リード線１４を接続した回路基板１３と、略釜形状の下ケーシング１５とを備える。回路基板１３は、ステータ部１７の反ポンプ部側付近に配置される。略釜形状の下ケーシング１５の凹部に、ロータ部２１が収まる。また、下ケーシング１５の凹部の中心部に、軸が嵌る軸孔１５ａを形成させている。 The stator portion 17 includes an iron core 10 formed by laminating electromagnetic steel plates, a winding 11 wound around a slot (not shown) of the iron core 10 via an insulator 12 (insulating member), and a lead wire 14. A connected circuit board 13 and a substantially casing-shaped lower casing 15 are provided. The circuit board 13 is disposed in the vicinity of the counter pump portion side of the stator portion 17. The rotor portion 21 is accommodated in the recess of the lower casing 15 having a substantially hook shape. A shaft hole 15 a into which the shaft is fitted is formed at the center of the recess of the lower casing 15.

特開２００８−２１５７３８号公報JP 2008-215738 A

（羽根有効長）
従来のヒートポンプ装置に使われるポンプ（特許文献１）では、軸支持部３５は逆円錐状を成した複数の脚状をなしている。そして、この軸支持部３５は、軸２７及びスラスト力を受けるスラストワッシャー２８の位置を保持するため、羽根プレート上２５ａの吸込穴３６の中に嵌め入れている。すなわち、羽根車２５の中央には吸入口２２とほぼ同等の径の吸込穴３６があけられている。そのため、その部分（吸込穴３６）の容積がポンプの液体圧送に対して無効となる。つまり吸込穴３６をあけたぶんだけ羽根２５ｃの有効長さが短くなるため、ポンプ効率向上の妨げとなるという課題があった。 (Effective blade length)
In a pump (Patent Document 1) used in a conventional heat pump device, the shaft support portion 35 has a plurality of leg shapes having an inverted conical shape. The shaft support 35 is fitted in the suction hole 36 of the blade plate top 25a in order to maintain the position of the shaft 27 and the thrust washer 28 that receives the thrust force. That is, a suction hole 36 having a diameter substantially equal to that of the suction port 22 is formed in the center of the impeller 25. Therefore, the volume of the portion (suction hole 36) becomes ineffective with respect to the liquid pumping of the pump. That is, the effective length of the blades 25c is shortened by the amount that the suction hole 36 is opened, which hinders improvement in pump efficiency.

（推力）
また羽根プレート上２５ａの吸込穴３６は、吸入口２２とほぼ同等の径であるため（吸込穴３６と吸入口２２との内径同士が略同じ）、羽根プレート下２５ｂより羽根プレート上２５ａ側の表面の面積が小さくなり、羽根車２５の上下に圧力差が生じ、推力が働く。そのため、この推力によるスラスト軸受の摺動による摩擦損失や、スラスト軸受の磨耗が大きく、ポンプ効率が低い、ポンプ寿命が短い、という課題があった。 (Thrust)
Further, the suction hole 36 on the blade plate upper 25a has substantially the same diameter as the suction port 22 (the inner diameters of the suction hole 36 and suction port 22 are substantially the same), so that the blade plate upper 25a side is closer to the blade plate upper 25a side. The surface area is reduced, a pressure difference is generated between the top and bottom of the impeller 25, and a thrust is applied. Therefore, there are problems that friction loss due to sliding of the thrust bearing due to this thrust force, wear of the thrust bearing is large, pump efficiency is low, and pump life is short.

（還流）
また羽根プレート上２５ａと上ケーシング２４との間に隙間があるため、羽根車２５によって外周方向に圧送された液体の一部が吐出口２３に向かわず吸入口２２へ還流して、ポンプ効率の低下を招くという課題があった。 (reflux)
Further, since there is a gap between the blade plate upper 25a and the upper casing 24, a part of the liquid pressure-fed by the impeller 25 in the outer circumferential direction returns to the suction port 22 without going to the discharge port 23, thereby improving the pump efficiency. There was a problem of causing a decrease.

この発明は、羽根有効長さを吸入口内径側に延長し、またスラスト軸受の摩擦損失を減らし、さらに吸入口への液体の還流を防止して、高効率で高寿命なポンプ及びヒートポンプ装置を提供することを目的とする。 This invention extends the effective blade length to the inner diameter side of the suction port, reduces the friction loss of the thrust bearing, and further prevents the liquid from flowing back to the suction port, thereby providing a highly efficient and long-life pump and heat pump device. The purpose is to provide.

この発明のポンプは、
液体を吸入する吸入口と、吸入された液体を吐出する吐出口とを備え、液体の吸入方向と吐出方向とが略直交するポンプにおいて、
前記吸入口の下方において、長手方向が前記吸入方向と略同じ方向になるように配置された軸と、
前記軸を中心に回転する円盤形状の羽根車であって、前記吸入方向から見た場合の前記円盤形状における中央の領域である中央領域以降から半径方向に放射状に形成された複数の羽根を有し、前記軸の方向を高さ方向とした場合に前記複数の羽根が前記吐出口と略同じ高さになるように配置され、前記軸を中心に回転することによって前記吸入口から液体を吸入して前記吐出口から吐出する羽根車と、
前記軸を受ける軸受であって、前記羽根車の前記中央領域に配置され、前記吸入口から吸入された液体を前記吐出口に案内する案内部を有すると共に、少なくとも一部が磁性材を含有する材料で形成された軸受と、
前記軸受よりも前記吸入口側となる上方で、前記吸入口の外周の領域に配置され、磁性材を含有する材料で形成された前記軸受を磁力によって前記上方に吸引する磁石部と
を備えたことを特徴とする。 The pump of this invention is
In a pump comprising a suction port for sucking liquid and a discharge port for discharging the sucked liquid, and the suction direction and the discharge direction of the liquid are substantially orthogonal,
Below the suction port, an axis arranged so that the longitudinal direction is substantially the same as the suction direction;
A disc-shaped impeller that rotates about the axis, and has a plurality of blades that are radially formed from the center region onward in the disc shape when viewed from the suction direction. When the direction of the shaft is the height direction, the plurality of blades are arranged so as to be substantially the same height as the discharge port, and the liquid is sucked from the suction port by rotating about the shaft. And an impeller that discharges from the discharge port;
A bearing for receiving the shaft, which is disposed in the central region of the impeller and has a guide portion for guiding the liquid sucked from the suction port to the discharge port, and at least a part thereof contains a magnetic material. Bearings made of material,
A magnet portion that is disposed in an outer peripheral region of the suction port above the bearing and closer to the suction port, and that attracts the bearing formed of a material containing a magnetic material upward by a magnetic force. It is characterized by that.

この発明により、磁気吸引力によって軸受けを吸引するので、吸入から吐出への還流を防止することができる。 According to the present invention, since the bearing is attracted by the magnetic attraction force, it is possible to prevent recirculation from suction to discharge.

実施の形態１におけるポンプ１１０の使用態様を示す図。FIG. 5 shows how the pump 110 is used in the first embodiment. 実施の形態１におけるポンプ１１０の断面図。Sectional drawing of the pump 110 in Embodiment 1. FIG. 実施の形態１における羽根車を説明するための図。FIG. 3 is a diagram for explaining the impeller in the first embodiment. 実施の形態１における吸入口２２のＸ方向矢視。The X direction arrow view of the suction inlet 22 in Embodiment 1. FIG. 実施の形態１における軸受１８−１の斜視図。The perspective view of the bearing 18-1 in Embodiment 1. FIG. 実施の形態１における軸受１８−１の平面図と正面図。The top view and front view of the bearing 18-1 in Embodiment 1. FIG. 実施の形態１における軸受１８−１の平面図。FIG. 3 is a plan view of a bearing 18-1 in the first embodiment. 実施の形態１における軸受１８−１のＢ−Ｂ断面、Ｃ−Ｃ断面。The BB cross section of the bearing 18-1 in Embodiment 1, and CC cross section. 実施の形態２におけるポンプ１２０の断面図。Sectional drawing of the pump 120 in Embodiment 2. FIG. 実施の形態２における軸受１８−２の斜視図。The perspective view of the bearing 18-2 in Embodiment 2. FIG. 実施の形態２における軸受１８−２の平面図。The top view of the bearing 18-2 in Embodiment 2. FIG. 実施の形態３におけるポンプ１３０の断面図。Sectional drawing of the pump 130 in Embodiment 3. FIG. 実施の形態３における上側軸受１８−３ａの斜視図。FIG. 10 is a perspective view of an upper bearing 18-3a in the third embodiment. 実施の形態３における上側軸受１８−３ａの平面図、断面図。The top view and sectional drawing of the upper side bearing 18-3a in Embodiment 3. FIG. 従来技術を示す図。The figure which shows a prior art.

実施の形態１．
図１〜図８を参照して実施の形態１のポンプ１１０を説明する。
図１は、実施の形態１のポンプ１１０の使用態様を示す図である。図１に示すように、
ポンプ１１０は例えばヒートポンプ装置に使用される。
図２は、ポンプ１１０の断面図（縦断面図）である。
図３は羽根車２５を説明するための図である。図３の（ａ）は、図２のＸ方向（液体の吸入方向）から見た場合の羽根車２５の羽根２５ｃの概要を示すための図である。図３の（ｂ）は、図３の（ａ）のＡ−Ａ断面である。
図４は、図２のＸ方向から見た場合の上ケーシングの軸孔２４ａの構成例を示す図である。図４では上ケーシングの軸孔２４ａは、４本の脚を持つ脚（２４ａ−１）を持つ形状としているが一例である。軸２７が嵌り、かつ、吸入される液体に対して大きな抵抗とならない形状であればよい。
図５はポンプ１１０の軸受（１８−１）の斜視図である。
図６は、軸受（１８−１）の平面図（Ｘ方向矢視相当）、正面図である
図７は、図６の平面図（図６の（ａ））に、破線で貫通孔（１８−１ｃ）を示した図である。
図８は、図６の（ｂ）におけるＢ−Ｂ断面、Ｃ−Ｃ断面を示す。 Embodiment 1 FIG.
The pump 110 according to the first embodiment will be described with reference to FIGS.
FIG. 1 is a diagram illustrating how the pump 110 according to the first embodiment is used. As shown in FIG.
The pump 110 is used for a heat pump device, for example.
FIG. 2 is a sectional view (longitudinal sectional view) of the pump 110.
FIG. 3 is a view for explaining the impeller 25. FIG. 3A is a diagram illustrating an outline of the blades 25c of the impeller 25 when viewed from the X direction (liquid suction direction) of FIG. FIG. 3B is an AA cross section of FIG.
4 is a diagram illustrating a configuration example of the shaft hole 24a of the upper casing when viewed from the X direction of FIG. In FIG. 4, the shaft hole 24a of the upper casing is an example having a shape having legs (24a-1) having four legs. Any shape that fits the shaft 27 and does not cause a large resistance to the liquid to be sucked may be used.
FIG. 5 is a perspective view of the bearing (18-1) of the pump 110. FIG.
6 is a plan view (corresponding to an arrow in the X direction) and a front view of the bearing (18-1), and FIG. 7 is a plan view of FIG. -1c).
FIG. 8 shows a BB cross section and a CC cross section in FIG.

（ヒートポンプ装置１００）
図１に示すように、ヒートポンプ装置１００は、冷媒を圧縮する圧縮機１、熱交換器３ａ，３ｂ等で構成される。ヒートポンプ装置１００は、冷媒９が流れる冷媒回路５を有する。例えば、熱交換器３ａは放熱器であり、熱交換器３ａ、熱交換器３ａによって加熱された温水を利用する熱利用機器１０１及びポンプ１１０が配管で接続されて、液体８が流れる液体回路４が構成される。熱利用機器１０１の例としては、液体を貯めておくタンクや、床暖房パネルなどの外部発熱体がある。 (Heat pump device 100)
As shown in FIG. 1, the heat pump device 100 includes a compressor 1 that compresses a refrigerant, heat exchangers 3a and 3b, and the like. The heat pump device 100 has a refrigerant circuit 5 through which the refrigerant 9 flows. For example, the heat exchanger 3a is a radiator, and a heat circuit 3a, a heat utilization device 101 that uses hot water heated by the heat exchanger 3a, and a pump 110 are connected by a pipe, and the liquid circuit 4 through which the liquid 8 flows. Is configured. Examples of the heat utilization device 101 include a tank for storing a liquid and an external heating element such as a floor heating panel.

（ポンプ１１０の構成）
ポンプ１１０は、軸２７及び上側の軸受（１８−１）がロータ部２１と一体となって回転する構成である。 (Configuration of pump 110)
The pump 110 is configured such that the shaft 27 and the upper bearing (18-1) rotate integrally with the rotor unit 21.

図２を用いてポンプ１１０の構成を説明する。ポンプ１１０は、ステータ部１７、ロータ部２１、ポンプ部２６、軸２７、及び吸入口２２の外周部に配置された磁石である吸入側磁石部２０１（磁石部）を備える。軸２７は固定（回転が拘束）されている。軸２７を中心に、ロータ部２１が回転する。 The configuration of the pump 110 will be described with reference to FIG. The pump 110 includes a suction portion magnet portion 201 (magnet portion) that is a magnet disposed on the outer peripheral portion of the stator portion 17, the rotor portion 21, the pump portion 26, the shaft 27, and the suction port 22. The shaft 27 is fixed (rotation is restricted). The rotor unit 21 rotates around the shaft 27.

（吸入側磁石部２０１）
上ケーシング２４の吸入口２２の外周部に、軸受（１８−１）を吸引させるための吸入側磁石部２０１を配置させる。軸受（１８−１）は、少なくとも一部が磁性材料で形成される。すなわち、軸受（１８−１）は、全体が磁性材料で形成されてもよいし、一部が磁性材料で形成されてもよく、例えば円筒部（１８−１ａ）のみが磁性材料で形成されてもよい。吸入側磁石部２０１は、形状が軸受（１８−１）の円筒部（１８−１ａ）を吸引可能であればどのような形状でも構わない。円筒部（１８−１ａ）は円筒状であるので、円筒部（１８−１ａ）の端面で均一に吸引させるには、吸入側磁石部２０１も円筒形状（例えば、板厚の厚いワッシャ形状）で、かつ、端面の各位相毎に磁束が均一に着磁したものが理想的である。吸入側磁石部２０１は、永久磁石でもよいし電磁石でもよい。図２は、吸入側磁石部２０１が電磁石の場合を示した。電磁石の場合、吸入側磁石部２０１は、図２の制御装置２０２によって、羽根車２５の回転数に応じて磁力が制御される。制御装置２０２は、回路基板１３に組み込まれたホール素子２０３によって検出されるマグネットの磁気から、羽根車２５の回転数を演算する。この制御は、詳細は実施の形態１の最後で後述する。吸入側磁石部２０１が電磁石の場合は、円筒状鉄心の外周にソレノイドコイルを構成させることで、端面部の磁束が均一なものが得られる。以下では、吸入側磁石部２０１は電磁石とする。 (Suction side magnet part 201)
A suction-side magnet portion 201 for attracting the bearing (18-1) is disposed on the outer peripheral portion of the suction port 22 of the upper casing 24. The bearing (18-1) is at least partially formed of a magnetic material. That is, the bearing (18-1) may be entirely formed of a magnetic material, or may be partially formed of a magnetic material. For example, only the cylindrical portion (18-1a) is formed of a magnetic material. Also good. The suction-side magnet unit 201 may have any shape as long as it can suck the cylindrical portion (18-1a) of the bearing (18-1). Since the cylindrical portion (18-1a) is cylindrical, the suction side magnet portion 201 is also cylindrical (for example, a thick washer shape) in order to uniformly attract the end surface of the cylindrical portion (18-1a). In addition, it is ideal that the magnetic flux is uniformly magnetized for each phase of the end face. The suction side magnet unit 201 may be a permanent magnet or an electromagnet. FIG. 2 shows a case where the suction side magnet unit 201 is an electromagnet. In the case of an electromagnet, the magnetic force of the suction side magnet unit 201 is controlled by the control device 202 of FIG. 2 according to the rotational speed of the impeller 25. The control device 202 calculates the rotational speed of the impeller 25 from the magnetism of the magnet detected by the Hall element 203 incorporated in the circuit board 13. Details of this control will be described later at the end of the first embodiment. When the suction-side magnet unit 201 is an electromagnet, a solenoid coil is formed on the outer periphery of the cylindrical iron core, so that a magnetic flux having a uniform end face can be obtained. Hereinafter, the suction side magnet unit 201 is an electromagnet.

（ステータ部１７）
（１）ステータ部１７の構成を説明する。ステータ部１７は、複数の所定の形状に打ち抜いた電磁鋼板を積層して形成される略ドーナッツ形状の鉄心１０と、この鉄心１０のスロット（図示せず）にインシュレータ（絶縁部材）１２を介して巻回される巻線１１と、リード線１４を接続した回路基板１３と、略釜形状の下ケーシング１５とを備える。回路基板１３は、ステータ部１７の一方の軸方向端部（反ポンプ部２６側）付近に配置される。（２）ステータ部１７は、巻線１１を巻いた鉄心１０と回路基板１３とをモールド樹脂１６を用いて一体成形され、ステータ部１７の外郭はモールド樹脂１６にて形成されている。（３）ステータ部１７と、ロータ部２１とで、例えば、ブラシレスＤＣモータを構成する。 (Stator part 17)
(1) The structure of the stator part 17 is demonstrated. The stator portion 17 includes a substantially donut-shaped iron core 10 formed by laminating a plurality of electromagnetic steel sheets punched into a predetermined shape, and an insulator (insulating member) 12 in a slot (not shown) of the iron core 10. A winding 11 to be wound, a circuit board 13 to which a lead wire 14 is connected, and a lower casing 15 having a substantially hook shape are provided. The circuit board 13 is disposed in the vicinity of one axial end portion (on the side opposite to the pump portion 26) of the stator portion 17. (2) The stator portion 17 is formed by integrally molding the iron core 10 around which the winding 11 is wound and the circuit board 13 by using a mold resin 16, and the outer periphery of the stator portion 17 is formed by the mold resin 16. (3) The stator portion 17 and the rotor portion 21 constitute, for example, a brushless DC motor.

（ロータ部２１）
ロータ部２１は、軸受（１８−１）、結合部材１９、磁石部２０からなる。中心部に軸受（１８−１）が配置され、軸受（１８−１）の外側に樹脂製の結合部材１９が配置され、結合部材１９の外側に結合部材１９で軸受（１８−１）と結合された磁石部２０が配置される。 (Rotor part 21)
The rotor unit 21 includes a bearing (18-1), a coupling member 19, and a magnet unit 20. A bearing (18-1) is disposed in the center, a resin coupling member 19 is disposed outside the bearing (18-1), and the coupling member 19 is coupled to the bearing (18-1) by the coupling member 19 outside the coupling member 19. The magnet part 20 made is arranged.

（ポンプ部２６）
ポンプ部２６は、吸入口２２、吐出口２３を有する上ケーシング２４と、羽根車２５とを備える。液体回路４は、吸入口２２と吐出口２３とに接続される。 (Pump unit 26)
The pump unit 26 includes an upper casing 24 having a suction port 22 and a discharge port 23, and an impeller 25. The liquid circuit 4 is connected to the suction port 22 and the discharge port 23.

略釜形状の下ケーシング１５の凹部に、ロータ部２１が収まる。また、下ケーシング１５の凹部の中心部に、軸２７が嵌る軸孔１５ａを形成されている。尚、軸２７は回転しないように、軸孔１５ａに挿入している。そのために、軸孔１５ａに挿入する軸２７の円形の一部を切り欠いている。 The rotor portion 21 is accommodated in the recess of the lower casing 15 having a substantially hook shape. A shaft hole 15 a into which the shaft 27 is fitted is formed at the center of the recess of the lower casing 15. The shaft 27 is inserted into the shaft hole 15a so as not to rotate. Therefore, a circular part of the shaft 27 inserted into the shaft hole 15a is cut out.

下ケーシング１５に固定された軸２７に、ロータ部２１の軸受（１８−１）を挿入し、更にその上部にスラストワッシャー２８を設置し、スラストワッシャー２８と軸受（１８−１）の端面（１８−１ｄ）は接触してスラスト軸受を形成する。そしてスラストワッシャー２８を貫通した軸２７のポンプ部２６側端部を、上ケーシング軸孔２４ａに挿入して上下ケーシングで囲われたポンプ部２６を構成する。羽根車２５を固定したロータ部２１は、軸２７の周囲に回転自在に配置される。 A bearing (18-1) of the rotor portion 21 is inserted into the shaft 27 fixed to the lower casing 15, and a thrust washer 28 is further installed on the shaft 27, and an end face (18 of the thrust washer 28 and the bearing (18-1) is provided. -1d) contact to form a thrust bearing. Then, the pump portion 26 side end portion of the shaft 27 penetrating the thrust washer 28 is inserted into the upper casing shaft hole 24a to constitute the pump portion 26 surrounded by the upper and lower casings. The rotor portion 21 to which the impeller 25 is fixed is rotatably disposed around the shaft 27.

下ケーシング１５と上ケーシング２４とで囲まれる空間は液体回路４の液体で満たされる。そのため、ロータ部２１、羽根車２５、軸２７、スラストワッシャー２８はポンプ１１０を流れる液体に触れる構造となっている。ポンプ１１０は、ポンプ１１０内部を流れる液体がブラシレスＤＣモータのロータ部２１に接するキャンド方式である。 A space surrounded by the lower casing 15 and the upper casing 24 is filled with the liquid of the liquid circuit 4. Therefore, the rotor unit 21, the impeller 25, the shaft 27, and the thrust washer 28 are configured to touch the liquid flowing through the pump 110. The pump 110 is a cand system in which the liquid flowing inside the pump 110 is in contact with the rotor part 21 of the brushless DC motor.

軸受（１８−１）は、羽根車２５の中心部（中心領域２５ｄ）を貫通し、羽根プレート上２５ａより吸入口２２側に突出した形状を成す。
軸受（１８−１）は、この突出した部分である円筒部（１８−１ａ）の外径は吸入口２２の内径と同等か、やや大きい径で、軸支持部より大きな径とする。円筒部（１８−１ａ）の上部の端面（１８−１ｄ）には、接触摺動させるスラストワッシャー２８を配置し、スラスト軸受を形成させる。スラストワッシャー２８は上ケーシング２４に回転方向に拘束した状態で軸受（１８−１）の端面（１８−１ｄ）に接触させている。このようにスラスト軸受を形成させることで、液体の吸入口２２への還流を防止する。更に軸受（１８−１）に軸直角方向に吸入口２２から羽根車２５を経由して吐出口２３に液体が流れる流路（案内部）を設ける。この流路は、例えば複数の貫通孔（１８−１ｃ）を羽根車２５の高さ位置に合わせて形成させている。
また、軸受（１８−１）の円筒部（１８−１ａ）の側面と、羽根プレート上２５ａの吸込穴３６の淵（破線で示す図２の範囲３７）とを摺接させることで、軸受（１８−１）に設けた貫通孔（１８−１ｃ）が羽根車２５の流路と連続した流路を成し、羽根２５ｃの有効長さを吸入口２２の内径側に延長することが可能となる。 The bearing (18-1) has a shape that penetrates the central portion (central region 25d) of the impeller 25 and protrudes from the blade plate top 25a to the suction port 22 side.
In the bearing (18-1), the cylindrical portion (18-1a), which is the protruding portion, has an outer diameter that is equal to or slightly larger than the inner diameter of the suction port 22 and is larger than the shaft support portion. A thrust washer 28 is provided on the end face (18-1d) at the upper part of the cylindrical portion (18-1a) to form a thrust bearing. The thrust washer 28 is brought into contact with the end face (18-1d) of the bearing (18-1) while being restrained in the rotational direction by the upper casing 24. By forming the thrust bearing in this manner, the reflux of the liquid to the suction port 22 is prevented. Furthermore, a flow path (guide portion) through which liquid flows from the suction port 22 to the discharge port 23 via the impeller 25 is provided in the bearing (18-1) in a direction perpendicular to the axis. In this flow path, for example, a plurality of through holes (18-1c) are formed in accordance with the height position of the impeller 25.
Further, the bearing (18-1) is slidably brought into contact with the side surface of the cylindrical portion (18-1a) of the bearing (18-1) and the flange (the range 37 in FIG. 2 indicated by a broken line) of the suction hole 36 on the blade plate 25a. The through-hole (18-1c) provided in 18-1) forms a flow path that is continuous with the flow path of the impeller 25, and the effective length of the blade 25c can be extended to the inner diameter side of the suction port 22. Become.

上述のように、更にこの内径に流路を設けたスラスト軸受を磁性材を含む材料で形成し、その上部の上ケーシングの吸入口外径部に磁石を設けて軸受けを吸引させることで、軸受、スラストワッシャー、上ケーシングとの密着が確実に確保される。 As described above, a thrust bearing provided with a flow path at the inner diameter is formed of a material containing a magnetic material, and a magnet is provided at the outer diameter portion of the suction port of the upper casing of the upper casing so as to attract the bearing. Adherence to the thrust washer and the upper casing is ensured.

また、従来は、羽根車２５の中央部の空洞部分には上ケーシング２４の軸支持部３５が入り込んでおり、羽根２５ｃの有効長さが短くなっていた。これに対してロータ部２１とともに回転する軸受（１８−１）に軸直角方向に流路となる貫通孔（１８−１ｃ）を設けたので、この流路が実質的に羽根２５ｃと同様に作用するので、内径側に羽根２５ｃを延長したのと同じ効果（シュラウドの効果）がある。 Further, conventionally, the shaft support portion 35 of the upper casing 24 has entered the hollow portion at the center of the impeller 25, and the effective length of the blade 25c has been shortened. On the other hand, since the bearing (18-1) that rotates together with the rotor portion 21 is provided with a through hole (18-1c) that becomes a flow path in a direction perpendicular to the axis, this flow path acts substantially like the blade 25c. Therefore, there is the same effect (shroud effect) as extending the blades 25c on the inner diameter side.

図面を参照して、ポンプ１１０の構成をさらに詳しく説明する。図２に示すように、ポンプ１１０は、液体を吸入する吸入口２２と、吸入された液体を吐出する吐出口２３とを備える。ポンプ１１０では、液体の吸入方向Ｘと吐出方向Ｙとが略直交する。ポンプ１１０は、軸２７、羽根車２５、軸受（１８−１）を備えている。軸２７は、吸入口２２の下方において、長手方向が吸入方向Ｘと略同じ方向になるように配置される。羽根車２５は、軸２７を中心に回転する円盤形状である。図３の（ａ）に示すように、羽根車２５は、吸入方向Ｘから見た場合の円盤形状における中央の領域である中央領域２５ｄ以降から半径方向に放射状に形成された複数の羽根２５ｃを有する。 The configuration of the pump 110 will be described in more detail with reference to the drawings. As shown in FIG. 2, the pump 110 includes a suction port 22 for sucking liquid and a discharge port 23 for discharging sucked liquid. In the pump 110, the liquid suction direction X and the discharge direction Y are substantially orthogonal. The pump 110 includes a shaft 27, an impeller 25, and a bearing (18-1). The shaft 27 is arranged below the suction port 22 so that the longitudinal direction is substantially the same as the suction direction X. The impeller 25 has a disk shape that rotates about a shaft 27. As shown in FIG. 3 (a), the impeller 25 includes a plurality of blades 25c that are radially formed in the radial direction from the central region 25d, which is the central region in the disk shape when viewed from the suction direction X. Have.

図２に示すように、羽根車２５は、軸２７の方向を高さ方向とした場合に複数の羽根２５ｃが吐出口２３と略同じ高さになるように配置される。ポンプ１１０は、軸２７を中心に羽根車２５と一体となったロータ部２１が回転することによって吸入口２２から液体を吸入して吐出口２３から吐出する。軸受（１８−１）は、軸２７を受ける。軸受（１８−１）は、羽根車２５の中央領域２５ｄに配置される案内部（流路）を有する。軸受（１８−１）では、案内部は貫通孔（１８９−１ｃ）である。貫通孔（１８−１ｃ）は、吸入口２２から吸入された液体を吐出口２３に案内する。貫通孔（１８−１ｃ）は、図５、図７、図８等に示すように、例えば、８個形成されているが、個数に制限はなくいくつでもよく、流路断面形状は任意でよく、また、内径から外径に向かって面積が大きくなっても構わない。 As shown in FIG. 2, the impeller 25 is arranged so that the plurality of blades 25 c have substantially the same height as the discharge port 23 when the direction of the shaft 27 is the height direction. The pump 110 sucks liquid from the suction port 22 and discharges it from the discharge port 23 when the rotor unit 21 integrated with the impeller 25 rotates around the shaft 27. The bearing (18-1) receives the shaft 27. The bearing (18-1) has a guide portion (flow path) disposed in the central region 25d of the impeller 25. In the bearing (18-1), the guide portion is a through hole (189-1c). The through hole (18-1c) guides the liquid sucked from the suction port 22 to the discharge port 23. As shown in FIGS. 5, 7, 8, etc., eight through holes (18-1 c) are formed, for example, but the number is not limited and any number may be used, and the channel cross-sectional shape may be arbitrary. Also, the area may increase from the inner diameter toward the outer diameter.

（シール性能）
また羽根車２５は、図２に示すように、羽根プレート上２５ａ、羽根プレート下２５ｂ及び複数の羽根２５ｃとから構成される。羽根プレート上２５ａは、円盤形状である羽根車２５の上側を構成し、中央部に吸入口２２から吸入される液体が吸い込まれる円形の開口である吸込穴３６（図３の（ａ））が形成されている。羽根プレート下２５ｂは、円盤形状の下側を構成し、羽根プレート上２５ａに対向して配置される。複数の羽根２５ｃは、羽根プレート上２５ａと羽根プレート下２５ｂとの間に形成されてもよいし、また、羽根２５ｃは羽根プレート上２５ａ又は羽根プレート下２５ｂと一体に形成しても構わない。
軸受（１８−１）は、図５に示すように、中空の円筒部（１８−１ａ）と、円筒部（１８−１ａ）の下側に引き続いて形成される中空厚肉の厚肉円筒部（１８−１ｂ）（案内部の一例）を備える。円筒部（１８−１ａ）は、図２に示すように、羽根プレート上２５ａの吸込穴３６に嵌り、かつ、側面が吸込穴３６の周縁に密着（図２の範囲３７）する。密着させる手段としては、例えば、溶着等を用いることができる。厚肉円筒部（１８−１ｂ）は、円筒部（１８−１ａ）の肉厚よりも厚い肉厚であり、軸２７に対して略直角方向にその肉厚部分に複数の貫通孔（１８−１ｃ）が形成されている。
ポンプ１１０では、円筒部（１８−１ａ）の側面が吸込穴３６の周縁に摺接（図２の範囲３７）するので、還流を防止できる。 (Seal performance)
As shown in FIG. 2, the impeller 25 includes an upper blade plate 25a, a lower blade plate 25b, and a plurality of blades 25c. The upper blade plate 25a constitutes the upper side of the disk-shaped impeller 25, and a suction hole 36 ((a) in FIG. 3) which is a circular opening into which the liquid sucked from the suction port 22 is sucked into the central portion. Is formed. The lower wing plate 25b constitutes the lower side of the disk shape and is disposed to face the upper wing plate 25a. The plurality of blades 25c may be formed between the blade plate upper portion 25a and the blade plate lower portion 25b, and the blade 25c may be formed integrally with the blade plate upper portion 25a or the blade plate lower portion 25b.
As shown in FIG. 5, the bearing (18-1) includes a hollow cylindrical part (18-1 a) and a hollow thick-walled cylindrical part formed subsequently on the lower side of the cylindrical part (18-1 a). (18-1b) (an example of a guide unit). As shown in FIG. 2, the cylindrical portion (18-1 a) fits into the suction hole 36 of the blade plate top 25 a and the side surface is in close contact with the periphery of the suction hole 36 (range 37 in FIG. 2). For example, welding or the like can be used as the means for the close contact. The thick cylindrical portion (18-1b) is thicker than the cylindrical portion (18-1a), and a plurality of through holes (18- 1c) is formed.
In the pump 110, since the side surface of the cylindrical portion (18-1a) is in sliding contact with the peripheral edge of the suction hole 36 (range 37 in FIG. 2), reflux can be prevented.

（スラスト軸受）
図２に示すように、ポンプ１１０は、吸入口２２が形成された上ケーシング２４と、上ケーシング２４によって軸２７まわりの回転を拘束されて支持されるスラストワッシャー２８とを備えている。軸受（１８−１）は、円筒部（１８−１ａ）の上側の端面（１８−１ｄ）と、スラストワッシャー２８と、スラストワッシャー２８を支持する上ケーシングの支持部２４ｂとによって、スラスト軸受を構成する。 (Thrust bearing)
As shown in FIG. 2, the pump 110 includes an upper casing 24 in which a suction port 22 is formed, and a thrust washer 28 supported by the upper casing 24 while being restricted from rotating about a shaft 27. The bearing (18-1) constitutes a thrust bearing by the upper end surface (18-1d) of the cylindrical portion (18-1a), the thrust washer 28, and the support portion 24b of the upper casing that supports the thrust washer 28. To do.

本実施の形態１の軸受（１８−１）は、１つの部品（図５参照）で、ラジアル方向とスラスト方向双方の軸受機能を併せ持つため、ラジアル、スラストを別々の軸受で受け持つ場合に比べて、寸法精度が高いという効果も有する。 Since the bearing (18-1) of the first embodiment is a single component (see FIG. 5) and has both the radial and thrust bearing functions, the radial and thrust bearings are handled separately by separate bearings. Also, it has an effect of high dimensional accuracy.

（材料）
（１）実施の形態１で用いられる材料は、例えば上ケーシング２４は、変性ポリフェニレンエーテル（以下ｍ−ＰＰＥ）やポリフェニレンスルファイド（以下ＰＰＳ）、シンジオタクチックポリスチレン（以下ＳＰＳ）などの耐熱水性、耐薬品性の熱可塑性樹脂で構成される。
（２）結合部材１９、羽根車２５（羽根プレート上２５ａ、羽根プレート下２５ｂ、羽根２５ｃ）もｍ−ＰＰＥ、ＰＰＳ、ＳＰＳ等の樹脂で構成される。
（３）下ケーシング１５はｍ−ＰＰＥ、ＰＰＳ、ＳＰＳ等の樹脂の他に、アルミ、ステンレス、銅などの金属を用いても良い。
（４）軸２７は、ステンレス、セラミックなどで構成される。（５）磁石部２０はフェライト系、ネオジウム系、サマリウム鉄窒素系等から選ばれる１種または複数を混合した磁粉とポリアミドやＰＰＳなどのバインダー樹脂と混合したプラスチック磁石部で構成される。
（６）軸受（１８−１）は、カーボンファイバーやフッソ樹脂を含有したＰＰＳなど摺動性、耐摩耗性に優れる熱可塑性樹脂にフェライト系、ネオジウム系、サマリウム鉄窒素系等から選ばれる１種または複数を混合した磁粉を混合させた材料で構成されている。
（７）なお結合部材１９（羽根プレート下２５ｂを含む）は軸受（１８−１）を同一材料で一体に成形しても良く、その場合は形状自由度の高い樹脂でかつ摺動性に優れるカーボンファイバーやフッソ樹脂を含有したＰＰＳで成形するのが好ましい。
（８）スラストワッシャー２８はセラミックやステンレスで構成されるが、カーボンファイバーやフッソ樹脂を含有したＰＰＳで構成しても良い。
（９）なお互いに接触摺動する軸受を構成する部位は同種材料ではなく、異種材料とした方がカジリ等が発生し難く好ましい。 (material)
(1) As for the material used in Embodiment 1, for example, the upper casing 24 is hot water resistant such as modified polyphenylene ether (hereinafter m-PPE), polyphenylene sulfide (hereinafter PPS), syndiotactic polystyrene (hereinafter SPS), Consists of chemical-resistant thermoplastic resin.
(2) The coupling member 19 and the impeller 25 (the upper blade plate 25a, the lower blade plate 25b, and the blade 25c) are also made of a resin such as m-PPE, PPS, or SPS.
(3) The lower casing 15 may be made of a metal such as aluminum, stainless steel, or copper in addition to a resin such as m-PPE, PPS, or SPS.
(4) The shaft 27 is made of stainless steel, ceramic, or the like. (5) The magnet part 20 is comprised by the plastic magnet part which mixed the magnetic powder which mixed 1 type or multiple selected from a ferrite type, a neodymium type, a samarium iron nitrogen type, etc., and binder resin, such as polyamide and PPS.
(6) The bearing (18-1) is a thermoplastic resin having excellent slidability and wear resistance, such as PPS containing carbon fiber or fluorine resin, and one selected from ferrite, neodymium, samarium iron nitrogen and the like. Or it is comprised with the material which mixed the magnetic powder which mixed several.
(7) The coupling member 19 (including the blade plate lower portion 25b) may be formed by integrally molding the bearing (18-1) with the same material. In that case, it is a resin having a high degree of freedom in shape and excellent in slidability. It is preferable to mold with PPS containing carbon fiber or fluorine resin.
(8) The thrust washer 28 is made of ceramic or stainless steel, but may be made of PPS containing carbon fiber or fluorine resin.
(9) The parts constituting the bearings that slide in contact with each other are preferably not different materials, but different materials are preferred because galling or the like is less likely to occur.

（制御装置２０２による吸入側磁石部２０１の制御）
図２に示すように、上ケーシング２４の吸入口２２の外周部には磁性材料を含有する材料で形成された軸受（１８−１）を吸引させる吸入側磁石部２０１（電磁石）を配置した。制御装置２０２は、羽根車２５の回転数に応じて、吸入側磁石部２０１の磁力の強さを制御する。前述のように、制御装置２０２は、ホール素子２０３の検出値に基づき羽根車２５の回転数を演算する。
（１）例えば、制御装置２０２は、ポンプ起動時には吸入側磁石部２０１の磁力をゼロとしておいてポンプの始動性に影響を与えないようにし、徐々に磁力を強めていく。
（２）また、制御装置２０２は、羽根車２５の回転数上昇により吸入と吐出との圧力差が増大し、スラスト推力が増えた場合には、吸入側磁石部２０１のコイルへ与える電気量（電圧・電流）を可変させて磁力を調整し、スラスト損失が増加しないように制御してもよい。
（３）あるいは、制御装置２０２は、羽根車２５が回転を開始すると磁力をゼロから次第に増大させ、羽根車２５が所定の回転数を超えた場合には、磁力を減少させるようにしてもよい。 (Control of the suction side magnet unit 201 by the control device 202)
As shown in FIG. 2, a suction side magnet portion 201 (electromagnet) for attracting a bearing (18-1) formed of a material containing a magnetic material is disposed on the outer peripheral portion of the suction port 22 of the upper casing 24. The control device 202 controls the strength of the magnetic force of the suction side magnet unit 201 according to the rotational speed of the impeller 25. As described above, the control device 202 calculates the rotational speed of the impeller 25 based on the detection value of the hall element 203.
(1) For example, the control device 202 sets the magnetic force of the suction-side magnet unit 201 to zero when starting the pump so as not to affect the startability of the pump, and gradually increases the magnetic force.
(2) Further, when the pressure difference between the suction and the discharge increases due to the increase in the rotational speed of the impeller 25 and the thrust thrust increases, the control device 202 supplies the amount of electricity to the coil of the suction side magnet unit 201 ( The magnetic force may be adjusted by changing the voltage / current to control the thrust loss not to increase.
(3) Alternatively, the control device 202 may gradually increase the magnetic force from zero when the impeller 25 starts rotating, and decrease the magnetic force when the impeller 25 exceeds a predetermined rotational speed. .

実施の形態１のポンプ１１０は、以上のような構成にしたため、スラスト軸受の摩擦損失を減らし、羽根有効長さを吸入口２２の内径側に延長すると共に吸入口２２への液体の還流を防止して高効率で高寿命なポンプ及びヒートポンプ装置の提供が可能となる。 Since the pump 110 according to the first embodiment is configured as described above, the friction loss of the thrust bearing is reduced, the effective blade length is extended to the inner diameter side of the suction port 22, and the liquid is prevented from flowing back to the suction port 22. Thus, it is possible to provide a highly efficient and long-life pump and heat pump device.

以上のように、羽根車２５の中央領域に吸入口２２から羽根車２５の外周側に流路を形成する軸受（１８−１）を磁性材料を含む材料で形成した。そして、軸受（１８−１）を、上ケーシング２４の吸入口２２の外周部に設置した吸入側磁石部２０１で吸引し、スラスト軸受を密接させる。これによって吸入から吐出への還流を防ぐことができる。吸入側磁石部２０１を電磁石とすることで、ポンプ始動時には磁力をゼロとし、磁気吸引力によりスラスト軸受の摩擦損失増加を防止することができる。また吸入側磁石部２０１（電磁石）の磁力がない時には、重力によりロータ部２１、羽根車２５は下方に下がっており、スラスト軸受は密着していない。しかし、羽根車２５の回転数上昇とともに、吸入される流体と吐出される流体との圧力差が増え、羽根車２５を軸方向上に押し上げる推力が増大しスラスト軸受が密着する。この状態で吸入側磁石部２０１と軸受（１８−１）に磁気吸引力が働くと摩擦損失が増大する。このため、高回転時には磁力を弱めるなど羽根車２５の回転数に応じた磁力制御を行う。理想的には、
「（重力）＝（吸入〜吐出の圧力差による推力）十磁気吸引力」
となるように、制御装置２０２は、吸入側磁石部２０１へ与える電力（電流、電圧）を制御することが好ましい。 As described above, the bearing (18-1) that forms the flow path from the suction port 22 to the outer peripheral side of the impeller 25 in the central region of the impeller 25 is formed of a material containing a magnetic material. And a bearing (18-1) is attracted | sucked by the suction side magnet part 201 installed in the outer peripheral part of the suction inlet 22 of the upper casing 24, and a thrust bearing is closely_contact | adhered. This can prevent recirculation from inhalation to ejection. By using the suction-side magnet unit 201 as an electromagnet, the magnetic force is zero when the pump is started, and an increase in friction loss of the thrust bearing can be prevented by the magnetic attractive force. When there is no magnetic force of the suction side magnet unit 201 (electromagnet), the rotor unit 21 and the impeller 25 are lowered downward due to gravity, and the thrust bearing is not in close contact. However, as the rotational speed of the impeller 25 increases, the pressure difference between the sucked fluid and the discharged fluid increases, the thrust that pushes the impeller 25 upward in the axial direction increases, and the thrust bearing comes into close contact. In this state, when a magnetic attractive force acts on the suction side magnet unit 201 and the bearing (18-1), friction loss increases. For this reason, the magnetic force control according to the rotation speed of the impeller 25 is performed, such as weakening the magnetic force at the time of high rotation. Ideally
"(Gravity) = (Thrust due to pressure difference between suction and discharge) + magnetic attraction"
Thus, the control device 202 preferably controls the power (current, voltage) applied to the suction side magnet unit 201.

実施の形態２．
実施の形態２は、軸受の構造が実施の形態１と異なる。実施の形態２の軸受（１８−２）は、実施の形態１の軸受（１８−１）に対して、流路となる複数の貫通孔を、複数の羽根（１８ｃ−２）とした構成である。それ以外は、実施の形態１と同様である。従って軸２７及び軸受（１８−２）は、実施の形態１と同様に、ロータ部２１と一体となって回転する。 Embodiment 2. FIG.
The second embodiment is different from the first embodiment in the structure of the bearing. The bearing (18-2) of the second embodiment has a configuration in which a plurality of through holes serving as flow paths are a plurality of blades (18c-2) with respect to the bearing (18-1) of the first embodiment. is there. The rest is the same as in the first embodiment. Therefore, the shaft 27 and the bearing (18-2) rotate integrally with the rotor portion 21 as in the first embodiment.

図９〜図１０を参照して実施の形態２のポンプ１２０を説明する。
図９は、実施の形態２のポンプ１２０の断面図である。
図１０は、軸受（１８−２）の斜視図である。軸受（１８−２）は、吸入口２２から吸入された液体を吐出口２３に案内する案内部として、複数の羽根（１８ｃ−２）を備えている。
図１１は、軸受（１８−２）の平面図（Ｘ方向矢視）である。 The pump 120 according to the second embodiment will be described with reference to FIGS.
FIG. 9 is a cross-sectional view of the pump 120 according to the second embodiment.
FIG. 10 is a perspective view of the bearing (18-2). The bearing (18-2) includes a plurality of blades (18 c-2) as a guide unit that guides the liquid sucked from the suction port 22 to the discharge port 23.
FIG. 11 is a plan view (as viewed in the X direction) of the bearing (18-2).

図９に示すように、ポンプ１２０も、吸入側磁石部２０１、制御装置２０２、ホール素子２０３を有する点は実施の形態１と同じである。また図１０の説明で後述する軸受（１８−２）は、実施の形態１の（１８−１）と同様に少なくとも一部が磁性材料を含む材料で形成されている。例えば、図１０に示すように、軸受（１８−２）の、羽根（１８ｃ−２）を含む上側部分（１８−２−１）のみを磁性材料を含む材料で形成してもよいし、上側部分（１８−２−１）と下側部分（１８−１−２）との、軸受（１８−２）の全体を磁性材料を含む材料で形成してもよいし。また、制御装置２０２が吸入側磁石部２０１に対して行う制御は、実施の形態１と同じである。 As shown in FIG. 9, the pump 120 is the same as that of the first embodiment in that it includes a suction side magnet unit 201, a control device 202, and a hall element 203. Further, the bearing (18-2), which will be described later in the description of FIG. 10, is formed of a material containing a magnetic material at least in part, similarly to (18-1) of the first embodiment. For example, as shown in FIG. 10, only the upper part (18-2-1) including the blade (18c-2) of the bearing (18-2) may be formed of a material containing a magnetic material, The whole of the bearing (18-2) of the part (18-2-1) and the lower part (18-1-2) may be formed of a material containing a magnetic material. The control performed by the control device 202 on the suction side magnet unit 201 is the same as that in the first embodiment.

図１０に示すように、軸受（１８−２）の一部に、軸直角方向に吸入口２２から羽根車２５を経由して吐出口２３に液体が流れる流路を、複数の羽根（１８ｃ−２）によって形成することによっても、実施の形態１の軸受（１８−１）と同等の効果を奏する。この場合、羽根（１８ｃ−２）は、羽根車２５の羽根２５ｃの形状に対応する形状としてもよい。すなわち、羽根（１８ｃ−２）は、羽根２５ｃが円弧やインボリュート曲線といった場合、同一の成型規則（同じ曲率半径あるいはインボリュート曲線で形成）で形成してもよい。軸受（１８−２）に設ける羽根（１８−２ｄ）の枚数は、羽根車２５の羽根２５ｃと同数か、それよりも多くても少なくても構わない。その他の構成は実施の形態１と同等である。 As shown in FIG. 10, a part of the bearing (18-2) is provided with a plurality of blades (18c−) through which a liquid flows from the suction port 22 to the discharge port 23 through the impeller 25 in a direction perpendicular to the axis. Also by forming according to 2), the same effect as the bearing (18-1) of the first embodiment can be obtained. In this case, the blade (18c-2) may have a shape corresponding to the shape of the blade 25c of the impeller 25. That is, the blade (18c-2) may be formed with the same molding rule (formed with the same curvature radius or involute curve) when the blade 25c is an arc or an involute curve. The number of blades (18-2d) provided on the bearing (18-2) may be the same as or more or less than the number of blades 25c of the impeller 25. Other configurations are the same as those of the first embodiment.

実施の形態３．
実施の形態３のポンプ１３０を説明する。実施の形態３のポンプ１３０は、実施の形態２の軸受軸受（１８−２）を、上側と下側とに２分割した場合を説明する。なお、ポンプ１３０では軸２７及び上側軸受（１８−３ａ）がロータ部２１と一体となって回転する。 Embodiment 3 FIG.
The pump 130 of Embodiment 3 is demonstrated. The pump 130 of Embodiment 3 demonstrates the case where the bearing (18-2) of Embodiment 2 is divided | segmented into the upper side and the lower side. In the pump 130, the shaft 27 and the upper bearing (18-3a) rotate integrally with the rotor portion 21.

図１２〜図１４を参照して、実施の形態３のポンプ１３０を説明する。 With reference to FIGS. 12-14, the pump 130 of Embodiment 3 is demonstrated.

図１２は、実施の形態３のポンプ１３０の断面図である。図１２、図１３に示すように、ポンプ１３０では、軸受は、上側軸受（１８−３ａ）と下側軸受（１８−３ｂ）との、上下２分割の構成である。上側軸受（１８−３ａ）は、吸入口２２側で軸２７の一方の端部を受けると共に案内部である複数の羽根（１８ｃ−３）（図１３）を有する。下側軸受（１８−３ｂ）は、吸入口２２の反対側で、軸２７の他方の端部を受ける。 FIG. 12 is a cross-sectional view of the pump 130 according to the third embodiment. As shown in FIGS. 12 and 13, in the pump 130, the bearing has a vertically divided structure of an upper bearing (18-3 a) and a lower bearing (18-3 b). The upper bearing (18-3a) has a plurality of blades (18c-3) (FIG. 13) that receive one end portion of the shaft 27 on the suction port 22 side and are guide portions. The lower bearing (18-3b) receives the other end of the shaft 27 on the opposite side of the suction port 22.

図１２に示すように、ポンプ１３０が、吸入側磁石部２０１、制御装置２０２、ホール素子２０３を有する点は実施の形態１と同じである。また上記のように、ポンプ１３０では、軸受は上下２分割の構成である。ポンプ１３０では、図１３に示す上側軸受（１８−２）が磁性材料を含む材料で形成されている。また、実施の形態３においても、制御装置２０２が吸入側磁石部２０１に対して行う制御は、実施の形態１と同じである。 As shown in FIG. 12, the pump 130 includes the suction side magnet unit 201, the control device 202, and the Hall element 203, which is the same as in the first embodiment. In addition, as described above, in the pump 130, the bearing has a structure that is divided into two parts in the vertical direction. In the pump 130, the upper bearing (18-2) shown in FIG. 13 is formed of a material containing a magnetic material. In the third embodiment, the control performed by the control device 202 on the suction side magnet unit 201 is the same as that in the first embodiment.

図１３は、上側軸受（１８−３ａ）の斜視図である。上側軸受（１８−３ａ）は、案内部である複数の羽根（１８ｃ−３）を有する。
図１４は正面図（図１のＸ方向矢視）およびＤ−Ｄ断面図である。 FIG. 13 is a perspective view of the upper bearing (18-3a). The upper bearing (18-3a) has a plurality of blades (18c-3) which are guide portions.
14 is a front view (in the direction of the arrow X in FIG. 1) and a DD cross-sectional view.

（ロータ部２１）
図１２に示すように、磁石部２０と軸２７とは結合部材１９で一体に成形される。また、結合部材１９は、羽根プレート下２５ｂを兼ねている。これら（磁石部２０、軸２７、結合部材１９）は、回転方向にも軸方向にも拘束固着し一体化されている。羽根プレート下２５ｂに、羽根２５ｃと羽根プレート上２５ａとが溶着などにより固着され一体となっている。このように、磁石部２０、結合部材１９、軸２７、上側軸受（１８−３ａ）等は、ロータを形成する。 (Rotor part 21)
As shown in FIG. 12, the magnet portion 20 and the shaft 27 are integrally formed by the coupling member 19. Moreover, the coupling member 19 also serves as the lower blade plate 25b. These (the magnet part 20, the shaft 27, and the coupling member 19) are fixed and integrated in both the rotational direction and the axial direction. The blade 25c and the blade plate upper 25a are fixed to and integrated with the lower blade plate 25b by welding or the like. Thus, the magnet part 20, the coupling member 19, the shaft 27, the upper bearing (18-3a) and the like form a rotor.

図１２に示すように、下ケーシング１５の軸穴１５ａには、下側軸受（１８−３ｂ）が回転方向に拘束された状態で嵌入される。下側軸受（１８−３ｂ）には、ロータ部２１と一体となった軸２７の下端部が回転自在の状態で挿入される。軸２７の上端部には、上側軸受（１８−３ａ）が軸２７に対して回転方向に拘束された状態で挿入される。すなわち、上側軸受（１８−３ａ）とロータ部２１とは一体に回転する。 As shown in FIG. 12, the lower bearing (18-3b) is fitted into the shaft hole 15a of the lower casing 15 in a state of being restrained in the rotational direction. The lower bearing (18-3b) is inserted with the lower end portion of the shaft 27 integrated with the rotor portion 21 in a rotatable state. The upper bearing (18-3a) is inserted into the upper end portion of the shaft 27 in a state of being restrained in the rotational direction with respect to the shaft 27. That is, the upper bearing (18-3a) and the rotor portion 21 rotate integrally.

（上側軸受（１８−３ａ））
図１３、図１４に示すように、上側軸受（１８−３ａ）の上部は三角錐形状を成し、吸入口２２の径の外側（下側）でスラストワッシャー２８とスラストおよびラジアル方向で接触摺動する。図１３では上側軸受（１８−３ａ）へのスラストワッシャー２８の取付状態を示している。スラストワッシャー２８は回転方向に拘束された状態で上ケーシング２４の吸入口２２に設置されている。スラストワッシャー２８を回転方向に拘束する方法は、例えば、図１３のように外周の一部をカットして切り欠き部２８−１を設け、上ケーシング２４の対向位置も同形状（スラストワッシャー２８の切り欠き部２８−１に対向する部分を同形状で凸）とする。上側軸受（１８−３ａ）の上部には図１３に示すように、羽根（１８ｃ−３）を設け、横断面形状（図１４の（ａ）に示す羽根（１８ｃ−３）の形状じ同じ）を羽根車２５の羽根２５ｃと近似した形状（略同一の形状）とし、枚数、位相も近似（略同一）させ、羽根（１８ｃ−３）（案内部）によって流路を形成する。その他の構成は実施の形態１と同等である。 (Upper bearing (18-3a))
As shown in FIGS. 13 and 14, the upper part of the upper bearing (18-3a) has a triangular pyramid shape, and is in contact with the thrust washer 28 on the outer side (lower side) of the diameter of the suction port 22 in the thrust and radial directions. Move. FIG. 13 shows a state in which the thrust washer 28 is attached to the upper bearing (18-3a). The thrust washer 28 is installed in the suction port 22 of the upper casing 24 while being restricted in the rotational direction. As a method of restraining the thrust washer 28 in the rotational direction, for example, as shown in FIG. 13, a part of the outer periphery is cut to provide a notch 28-1, and the opposing position of the upper casing 24 has the same shape (the thrust washer 28 of The portion facing the notch 28-1 is convex in the same shape). As shown in FIG. 13, the upper bearing (18-3a) is provided with a blade (18c-3) as shown in FIG. 13, and has a cross-sectional shape (the same shape as the blade (18c-3) shown in FIG. 14A). The shape is approximated (substantially the same shape) as the blade 25c of the impeller 25, the number and phase are also approximated (substantially the same), and the flow path is formed by the blade (18c-3) (guide portion). Other configurations are the same as those of the first embodiment.

実施の形態３の構成によっても、実施の形態１と同様の効果を得ることができる。 Also by the configuration of the third embodiment, the same effect as that of the first embodiment can be obtained.

以上の実施の形態１〜３で説明したポンプ１１０〜１４０は、ヒートポンプ装置１００内の液体を搬送、循環させる時に使用するポンプ２の例を示したが、家庭用ポンプなどにも利用可能である。 The pumps 110 to 140 described in the above first to third embodiments are examples of the pump 2 that is used when transporting and circulating the liquid in the heat pump apparatus 100. However, the pumps 110 to 140 can also be used for home pumps and the like. .

１圧縮機、３ａ，３ｂ熱交換器、４液体回路、５冷媒回路、８液体、９冷媒、１０鉄心、１１巻線、１２インシュレータ（絶縁部材）、１３回路基板、１４リード線、１５下ケーシング、１５ａ下ケーシング軸孔、１６モールド樹脂、１７ステータ部、１８−１，１８−２軸受、１８−３ａ，１８−４ａ上側軸受、１８−３ｂ，１８−４ｂ下側軸受、１８−１ａ円筒部、１８−１ｂ厚肉円筒部、１８−１ｃ貫通孔、１８−１ｄ端面、１８ｃ−２，１８ｃ−３，１８ｃ−４羽根、１９結合部材、２０磁石部、２１ロータ部、２２吸入口、２３吐出口、２４上ケーシング、２４ａ軸孔、２４ａ−１脚、２４ｂ支持部、２５羽根車、２５ａ羽根プレート上、２５ｂ羽根プレート下、２５ｃ羽根、２５ｄ中央領域、２６ポンプ部、２７軸、２８スラストワッシャー、３０流路、３５軸支持部、３６吸込穴、３７範囲、１００ヒートポンプ装置、１０１熱利用機器、１１０，１２０，１３０，１４０ポンプ、２０１吸入側磁石部、２０２制御装置、２０３ホール素子。 DESCRIPTION OF SYMBOLS 1 Compressor, 3a, 3b Heat exchanger, 4 Liquid circuit, 5 Refrigerant circuit, 8 Liquid, 9 Refrigerant, 10 Iron core, 11 Winding, 12 Insulator (insulation member), 13 Circuit board, 14 Lead wire, 15 Lower casing , 15a Lower casing shaft hole, 16 Mold resin, 17 Stator part, 18-1, 18-2 bearing, 18-3a, 18-4a Upper bearing, 18-3b, 18-4b Lower bearing, 18-1a Cylindrical part , 18-1b Thick cylindrical portion, 18-1c through hole, 18-1d end face, 18c-2, 18c-3, 18c-4 blade, 19 coupling member, 20 magnet portion, 21 rotor portion, 22 suction port, 23 Discharge port, 24 upper casing, 24a shaft hole, 24a-1 leg, 24b support, 25 impeller, 25a on blade plate, 25b below blade plate, 25c blade, 5d central region, 26 pump part, 27 shaft, 28 thrust washer, 30 flow path, 35 shaft support part, 36 suction hole, 37 range, 100 heat pump device, 101 heat utilization device, 110, 120, 130, 140 pump, 201 Suction side magnet section, 202 control device, 203 hall element.

Claims

In a pump comprising a suction port for sucking liquid and a discharge port for discharging the sucked liquid, and the suction direction and the discharge direction of the liquid are substantially orthogonal,
Below the suction port, an axis arranged so that the longitudinal direction is substantially the same as the suction direction;
A disc-shaped impeller that rotates about the axis, and has a plurality of blades that are radially formed from the center region onward in the disc shape when viewed from the suction direction. When the direction of the shaft is the height direction, the plurality of blades are arranged so as to be substantially the same height as the discharge port, and the liquid is sucked from the suction port by rotating about the shaft. And an impeller that discharges from the discharge port;
A bearing for receiving the shaft, which is disposed in the central region of the impeller and has a guide portion for guiding the liquid sucked from the suction port to the discharge port, and at least a part thereof contains a magnetic material. Bearings made of material,
A magnet portion that is disposed in an outer peripheral region of the suction port above the bearing and is closer to the suction port than the bearing, and that attracts the bearing formed of a material containing a magnetic material upward by a magnetic force ;
An upper casing in which the inlet is formed;
A thrust washer supported by the upper casing to be restrained from rotating about the axis;
With
The magnet part is
A pump characterized in that the annular end surface of the bearing facing one surface of the thrust washer is brought into close contact with the one surface of the thrust washer by attracting the bearing upward with a magnetic force .

The bearing is
2. The pump according to claim 1, wherein the whole is made of a material containing a magnetic material.

The magnet part is
3. The pump according to claim 1 , wherein the pump is an electromagnet that generates a magnetic force by supplying electric power.

The magnet part is
4. The pump according to claim 3, wherein the strength of the magnetic force is controlled according to the number of rotations of the impeller by the control of the control device.

The magnet part is
The pump according to claim 4, wherein the magnetic force gradually increases from zero when the impeller starts rotating under the control of the control device.

The magnet part is
6. The pump according to claim 5, wherein when the impeller starts rotating by the control device, the magnetic force gradually increases from zero, and when the predetermined rotational speed is exceeded, the magnetic force decreases.

In a pump comprising a suction port for sucking liquid and a discharge port for discharging the sucked liquid, and the suction direction and the discharge direction of the liquid are substantially orthogonal,
Below the suction port, an axis arranged so that the longitudinal direction is substantially the same as the suction direction;
A disc-shaped impeller that rotates about the axis, and has a plurality of blades that are radially formed from the center region onward in the disc shape when viewed from the suction direction. When the direction of the shaft is the height direction, the plurality of blades are arranged so as to be substantially the same height as the discharge port, and the liquid is sucked from the suction port by rotating about the shaft. And an impeller that discharges from the discharge port;
A bearing for receiving the shaft, which is disposed in the central region of the impeller and has a guide portion for guiding the liquid sucked from the suction port to the discharge port, and at least a part thereof contains a magnetic material. Bearings made of material,
A magnet portion that is disposed in an outer peripheral region of the suction port above the bearing and on the suction port side and that attracts the bearing formed of a material containing a magnetic material upward by a magnetic force;
With
The impeller is
An upper blade plate having a suction hole which is a circular opening into which a liquid sucked from the suction port is sucked in a central portion;
Comprising the lower side of the disk shape, and comprising a lower blade plate disposed opposite the upper blade plate,
The plurality of blades are formed between the upper blade plate and the lower blade plate,
The bearing is
Wherein fitted into the suction hole of the upper wing plate, and which has a hollow cylindrical portion side is brought into close contact with the peripheral edge of the suction hole, wherein the to Lupo pump to rotate in the impeller integrally.

The bearing is
The guide portion is a thick cylindrical portion formed continuously below the cylindrical portion and thicker than the thickness of the cylindrical portion, wherein the thickness is substantially perpendicular to the axis. 8. The pump according to claim 7, further comprising a thick cylindrical portion in which a plurality of through holes are formed.

The pump is
An upper casing in which the inlet is formed;
A thrust washer supported by the upper casing to be restrained from rotating about the axis,
The bearing is
9. The thrust bearing according to claim 7, wherein a thrust bearing is configured by the upper end surface of the cylindrical portion, the thrust washer, and the support portion of the upper casing that supports the thrust washer. pump.

In a pump comprising a suction port for sucking liquid and a discharge port for discharging the sucked liquid, and the suction direction and the discharge direction of the liquid are substantially orthogonal,
Below the suction port, an axis arranged so that the longitudinal direction is substantially the same as the suction direction;
A disc-shaped impeller that rotates about the axis, and has a plurality of blades that are radially formed from the center region onward in the disc shape when viewed from the suction direction. When the direction of the shaft is the height direction, the plurality of blades are arranged so as to be substantially the same height as the discharge port, and the liquid is sucked from the suction port by rotating about the shaft. And an impeller that discharges from the discharge port;
A bearing for receiving the shaft, which is disposed in the central region of the impeller and has a guide portion for guiding the liquid sucked from the suction port to the discharge port, and at least a part thereof contains a magnetic material. Bearings made of material,
A magnet portion that is disposed in an outer peripheral region of the suction port above the bearing and on the suction port side and that attracts the bearing formed of a material containing a magnetic material upward by a magnetic force;
With
The bearing is
As the guide portion, characteristics and to Lupo pump further comprising a plurality of blades.

The bearing is
The pump according to claim 10 , wherein the shape of the plurality of blades is a shape corresponding to the shape of the blades of the impeller.

Heat pump device having a pump according to any one of claims 1 to 11.